EP3043054A1 - Insert annulaire pour chemise de cylindre - Google Patents

Insert annulaire pour chemise de cylindre Download PDF

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Publication number
EP3043054A1
EP3043054A1 EP15150637.5A EP15150637A EP3043054A1 EP 3043054 A1 EP3043054 A1 EP 3043054A1 EP 15150637 A EP15150637 A EP 15150637A EP 3043054 A1 EP3043054 A1 EP 3043054A1
Authority
EP
European Patent Office
Prior art keywords
cuff
ring
top end
protrusion
recess
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.)
Granted
Application number
EP15150637.5A
Other languages
German (de)
English (en)
Other versions
EP3043054B1 (fr
Inventor
Sascha Burkhard
Eike Joachim Sixel
Hendrik Johannes Lange
Kai Ruschmeyer
Marius Wolfgramm
Andreas Banck
Dirk Mooser
Volker Abraham
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.)
Caterpillar Motoren GmbH and Co KG
Original Assignee
Caterpillar Motoren GmbH and Co KG
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.)
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Publication date
Application filed by Caterpillar Motoren GmbH and Co KG filed Critical Caterpillar Motoren GmbH and Co KG
Priority to EP15150637.5A priority Critical patent/EP3043054B1/fr
Publication of EP3043054A1 publication Critical patent/EP3043054A1/fr
Application granted granted Critical
Publication of EP3043054B1 publication Critical patent/EP3043054B1/fr
Active legal-status Critical Current
Anticipated expiration legal-status Critical

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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 
    • F02F1/004—Cylinder liners
    • 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

Definitions

  • the present disclosure relates to a cuff-ring for a cylinder liner of an internal combustion engine, and more particularly, to a cuff-ring with an uneven top end.
  • Cuff-rings are also known as fire rings, flame rings, carbon scraping rings, scraping rings or anti-polishing rings
  • Internal combustion engines such as diesel, gasoline and/or gaseous fuel engines, typically include a cylinder liner for guiding a piston disposed in an engine block.
  • the piston is designed with a small distance from the cylinder liner.
  • a lubricating film disposed on an inner surface of the cylinder liner reduces friction between the piston, associated piston rings and the cylinder liner.
  • soot and other particulates may accumulate on the piston, scavenge the inner surface of the cylinder liner, thereby reduce the lubricating film, which, in turn, may cause the engine to malfunction or break down.
  • Accumulation of particulates on the piston is usually avoided using a carbon scraping ring positioned in a top part of the cylinder liner.
  • the carbon scraping ring typically is positioned at a small distance away from a cylinder head of the internal combustion engine to avoid contact between the cylinder head and the carbon scraping ring due to thermal expansion and tolerances of other related engine parts.
  • US 6,164,260 of Caterpillar Inc. discloses a carbon scraping ring installed in a recess of a cylinder liner. When installed in the recess, the carbon scraping ring is positioned slightly away from the cylinder head such that during operation of the internal combustion engine no contact between the cylinder head and the carbon scraping ring occurs.
  • the present disclosure is directed, at least in part, to improving or overcoming one or more aspects of prior systems.
  • a cuff-ring for a cylinder liner of an internal combustion engine may comprise a cuff-ring axis, a circumferential outer side extending about the cuff-ring axis and being configured to contact the cylinder liner, a circumferential inner side extending about the cuff-ring axis and being configured to scrape off deposits accumulated on a piston of the internal combustion engine.
  • the cuff-ring may futher comprise a top end extending in radial direction between the circumferential inner side and the circumferential outer side, and a bottom end opposite the top end. The top end may include at least one of a protrusion or a recess.
  • an internal combustion engine comprises a piston, a cylinder liner for guiding the piston, a cylinder head, and a cuff-ring.
  • the cuff-ring may be configured to be positioned in the cylinder liner and may include a cuff-ring axis, a circumferential outer side extending about the cuff-ring axis and being configured to contact the cylinder liner, a circumferential inner side extending about the cuff-ring axis and being configured to scrape off deposits accumulated on the piston, a top end, and a bottom end opposite the top end, wherein the top end of the cuff-ring may include at least one of a protrusion or a recess.
  • the present disclosure is based in part on the realization that a clearance distance between the carbon scraping ring and the cylinder head constitutes a crevice volume which may result in an incomplete combustion and increased emissions such as unburned hydrocarbons.
  • the present disclosure may, therefore, further be based in part on the realization that a cuff-ring may be position closer to the cylinder head to reduce the crevice volume between the cylinder head and the cuff-ring. However, by reducing the crevice volume, the cuff-ring and the cylinder head may contact each other during operation of the internal combustion engine, thereby potentially causing the cuff-ring to deform or misalign.
  • the present disclosure may, therefore, further be based in part on the realization that deformation or misalignment between the cylinder head and the cuff-ring may be reduced by reducing a contact surface between the cylinder head and the cuff-ring.
  • a compression force between the cylinder head and the cuff-ring may be reduced, which, in turn, may reduce material deformation of the cuff-ring, and therefore a risk of potential misalignment of the cuff-ring during operation of the internal combustion engine.
  • the present disclosure may further be based in part on the realization that a contact surface between the cylinder head and the cuff-ring may be reduced by forming a top end of the cuff-ring with protrusions and/or recesses.
  • the protrusions and/or recesses define a distal end having an area smaller than a top end area of the cuff-ring without protrusions and/or recesses.
  • the present disclosure may further be based in part on the realization that a contact surface between the cylinder head and the cuff-ring may be minimized by providing a line contact between the cylinder head and the cuff-ring.
  • Internal combustion engine 1 may be any known type of internal combustion engine, having any shape and any number of cylinders.
  • Internal combustion engine 1 comprises a piston 2 and a cylinder liner 3.
  • Piston 2 and cylinder liner 3 are installed in a cylinder (not shown) of internal combustion engine 1.
  • a cylinder head 4 closes off the cylinder from on top.
  • Cylinder head 4 is in sealing contact with cylinder liner 3 using a cylinder head sealing 5.
  • Cylinder head sealing 5 seals off a sealing gap 51 between cylinder head 4 and cylinder liner 3.
  • Cylinder head sealing 5 may be any type of sealing known to a person skilled in the art.
  • Piston 2 may be provided with annular grooves 8.
  • piston rings 9 may be installed to seal the cylinder and regulate a flow of lubricant within the cylinder.
  • Cylinder liner 3 is designed with a small distance 6 away from piston 2 and seized to securely guide piston 2 during its reciprocating movement from top dead center (TDC) to bottom dead center (BDC), and vice versa. Cylinder liner 3 further comprises an inner surface 7. Inner surface 7 may comprise a micro-structure adapted to facilitate adhesion of a lubricating film, such as an oil film. Cylinder liner 3 may be manufactured from gray cast iron or other cast irons.
  • Liner recess 10 may comprise a fillet 11, preferably an arcuate fillet having at least one radius, more preferably two radii for reducing tension and crevice volume in liner recess 10.
  • a cuff-ring 12 is positioned in liner recess 10.
  • cuff-ring 12 may also be integrally formed with cylinder liner 3.
  • Cuff-ring 12 comprises a cuff-ring axis (shown in Fig. 2 ), a circumferential outer side 13 and a circumferential inner side 14.
  • Circumferential outer side 13 contacts cylinder liner 3 when positioned in liner recess 10, whereas circumferential inner side 14 faces piston 2.
  • circumferential inner side 14 is arranged closer to piston 2 than inner surface 7 of cylinder liner 3.
  • Circumferential inner side 14 may therefore constitute a scraping face configured to scrape off deposits accumulated on a side surface 15 of piston 2 during upward movement of piston 2 from BDC to TDC.
  • piston 2 is shown to be in TDC.
  • piston 2 may comprise a top part 16 formed with a taper.
  • Cuff-ring 12 may be manufactured from the same or different materials as cylinder liner 3, such as gray cast iron or other cast irons. Moreover, cuff-ring 12 may be designed such that during operation of internal combustion engine 1 cuff-ring 12 is press-fitted in liner recess 10.
  • Cuff-ring 12 further comprises a top end 17 indicated by a dashed line.
  • cuff-ring 12 may further comprise a protrusion 18 with a distal end 19.
  • Protrusion 18 extends in axial direction from top end 17 towards cylinder head 4.
  • top end 17 is explained in more detail when referring to Fig. 3 to 7 .
  • Top end 17 may have a first clearance distance 20 from cylinder head 4.
  • Protrusion 18 at its distal end 19 may have a second clearance distance 21 from cylinder head 4.
  • second clearance distance 21 may be significantly smaller, preferably about 50 % - 70 % or more, than first clearance distance 20.
  • first clearance distance is shown in Fig. 1 to have the same size as sealing gap 51, this may not necessarily be the case.
  • first clearance distance may be smaller than sealing gap 51 and, therefore, top end 17 may extend in axial direction beyond cylinder liner 3.
  • a contact between top end 17 of cuff-ring 12 and cylinder head 4 may occur more likely during operation of internal combustion engine 1.
  • the contact may be caused, for example, due to thermal expansion of cuff-ring 12.
  • cuff-ring 12 may expand in axial direction by about 0.5 mm or more, which is about the same size as current manufacturing tolerances.
  • a compression force between cuff-ring 12 and cylinder head 4 may build up - transmitted via top end 17.
  • the compression force may cause cuff-ring 12 to deform, which, in turn, may lead to a contact between circumferential inner side 14 and side surface 15, causing increased material wear and piston seizure, which may lead to a malfunction or break down of internal combustion engine 1. It was, however, realized that the compression force between cuff-ring 12 and cylinder head 4 may be reduced, when top end 17 is adapted such that the resulting contact surface between cylinder head 4 and cuff-ring 12 is smaller than an area of top end 17.
  • the contact surface is reduced by forming top end 17 with protrusion 18.
  • a potential contact surface between cylinder head 4 and top end 17 is reduced compared to an area defined by distal end 19.
  • Fig. 2 a schematic drawing of a cut through cuff-ring 12 is shown. Elements already explained in connection with Fig. 1 have the same reference numerals.
  • cuff-ring 12 comprises cuff-ring axis A, circumferential outer side 13 and circumferential inner side 14.
  • Circumferential outer side 13 contacts cylinder liner 3 when positioned in liner recess 10, and circumferential inner side 14 faces side surface 15 of piston 2.
  • circumferential inner side 14 and circumferential outer side 13 extend in radial direction about cuff-ring axis A, forming a closed ring.
  • Cuff-ring 12 further comprises top end 17 and a bottom end 23 opposite top end 17.
  • FIG. 3 to 8 are schematic views of cross-sectional cuts through cuff-ring 12 in a radial plane about cuff-ring axis A.
  • top end 17 includes protrusion 18.
  • Protrusion 18 may have a trapezoidal shape when viewed in a radial plane of cuff-ring axis A, but may have a different shape when viewed in a different radial plane. However, this may not necessarily be the case.
  • the trapezoidal shape may be a right trapezoid, as shown in Fig. 3 , having a first leg 181 extending in radial direction between circumferential inner side 14 and circumferential outer side 13, and a second leg 182 extending in axial direction from top end 17 in parallel to cuff-ring axis A.
  • First leg 181 may be formed, for example, by a chamfer or a bevel.
  • the trapezoidal shape may further comprise a distal end 19.
  • Distal end 19 has the largest distance from top end 17, when viewed in axial direction. During a potential contact between cuff-ring 12 and cylinder head 4, distal end 19, therefore, defines the contact surface. As can be easily seen, distal end 19 defines an area that is significantly smaller than an area defined by top end 17 during a potential contact with cylinder head 4. Thus, for a potential contact between cylinder head 4 and cuff-ring 12, the contact surface between the cylinder head 4 and distal end 19 is significantly smaller than the contact surface between the cylinder head 4 and top end 17, for example about 70 % to 85 % smaller. In Fig. 3 , distal end 19 is running horizontally between first leg 181 and second leg 182.
  • distal end 19 may run at an angle between first leg 181 and second leg 182, thereby reducing the contact surface further.
  • Protrusion 18 may have an axial extension from top end 17 that is about 5 % - 10 %, or less, of the radial extension between circumferential inner side 14 and circumferential outer side 13 and/or about 2 % - 5 %, or less, of the axial extension between top end 17 and bottom end 23 of cuff-ring 12.
  • Fig. 4 shows another embodiment of protrusion 18, where second leg 182 does not extend in axial direction from top end 17, but runs, with respect to top end 17, at an angle ⁇ towards distal end 19. Moreover, in the embodiment shown in Fig. 4 , first and second legs 181, 182 run at the same angle ⁇ towards each other, thereby defining a protrusion which, when viewed in a radial plane of the cuff-ring axis A, corresponds to an isosceles trapezoid.
  • first and second legs 181, 182 may run at different angles towards each other.
  • protrusion 18 In Fig. 5 another embodiment of protrusion 18 is shown where, when viewed in a radial plane of cuff-ring axis A, protrusion 18 has a triangular shape with a distal end 19 formed as a tip. Thus, during a potential contact between cuff-ring 12 and cylinder head 4, the contact surface reduces to a contact line, thereby minimizing the compression force further.
  • the triangular shape is an isosceles triangle and protrusion 18 may have an axial extension from top end 17 that is about 1 % - 2.5 %, or less, of the axial extension between top end 17 and bottom end 23 of cuff-ring 12.
  • the triangular shape may be an equilateral triangle, a right triangle, an acute triangle, or any other suitable triangle.
  • distal end 19 may not be centered between circumferential outer and inner sides 13, 14, as shown in Fig. 5 , but biased to either circumferential inner side 14 or circumferential outer side 13.
  • distal end 19 may be biased towards circumferential inner side 14 or, ideally, may be radially in-line with circumferential inner side 14, thereby arriving at a right triangle with first leg 181 running in axial direction from top end 17 in parallel with cuff-ring axis A.
  • protrusion 18 has, when viewed in a radial plane of cuff-ring axis A, the shape of a rectangle with at least one rounded edge 183 and a distal end 19.
  • Rounded edge 183 connects circumferential inner side 14 and distal end 19 in an arcuate shape.
  • the arcuate shape preferably, is formed by at least one convex radius, such as two or three convex radii, each being the same or different.
  • the arcuate shape may further include a concave radius, or a plurality of concave radii alternating with the plurality of convex radii.
  • FIG. 7 an embodiment is shown where, when viewed in a radial plane of cuff-ring axis A, top end 17 comprises a recess 25.
  • recess 25 has an arcuate shape.
  • the arcuate shape may be formed by at least one concave radius, such as one or two concave radii.
  • the arcuate shape may further comprise a convex radius interspaced between two adjacent concave radii, thereby arriving at a wave-like shape.
  • recess 25 may be formed by a plurality of grooves spaced apart in radial direction between circumferential outer and inner sides 13, 14.
  • Recess 25 discontinues top end 17 in that, when recess 25 is formed on top end 17, top end 17 no longer is entirely planar. Recess 25, therefore, defines a plurality of distal ends 19 between circumferential outer side 13 and circumferential inner side 14. Thus, by forming top end 17 with recess 25, distal ends 19 define a contact surface that is smaller than an area of top end 17 without recess 25 formed thereon. As a consequence, during a potential contact between cylinder head 4 and cuff-ring 12, a contact surface between cylinder head 4 and cuff-ring 12 is reduced.
  • top end 17 may extend in axial direction further towards cylinder head 4 than it would extend without recess 25 formed thereon, thereby reducing a crevice volume and a potential contact surface at the same time.
  • Fig. 8 shows an embodiment, where alternatively or in addition to modifications of top end 17, bottom end 23 is connected to circumferential outer side 13 by an arcuate fillet 26.
  • Arcuate fillet 26 includes a first radius 27 and a second radius 28, wherein, preferably, first radius 27 is smaller than second radius 28.
  • arcuate fillet 26, as well as first and second radii 27, 28, may be formed to fit in liner recess 10, such that, when cuff-ring 12 is positioned in liner recess 10, circumferential outer side 13 contacts cylinder liner 3 with a minimized crevice volume between cuff-ring 12 and cylinder liner 3.
  • the cuff-ring as generally disclosed herein is applicable in any internal combustion engine using a cylinder liner. If cuff-ring comprises an arcuate fillet connecting a bottom side with a circumferential outer side of the cuff-ring, the cuff-ring may be adjusted such that it fits into a corresponding recess formed on the cylinder liner.
  • Cuff-rings explained in connection with Fig. 3 to 8 are applicable, but not limited to diesel internal combustion engines of the series M20, M25, M32 and M43, to gaseous fuel engines of the series GCM34 and/or Dual fuel engines of the series M34DF and M46DF manufactured by Caterpillar Motoren GmbH & Co KG. However, other internal combustion engines may be used as well.
  • soot or other particulates may accumulate on side surface 15 of piston 2.
  • Cuff-ring 12, which is positioned in liner recess 10 of cylinder liner 3, may prevent particulate accumulation.
  • cuff-ring 12 is positioned in liner recess 10 such that circumferential inner side 14 protrudes further towards piston 2, in particular towards side surface 15 of piston 2, than inner surface 7 of cylinder liner 3.
  • circumferential inner side 14 may constitute a scraping face configured to scrape off deposits accumulated on side surface 15. Scraping of deposits occurs during upward movement of piston 2 from BDC to TDC, when circumferential inner side 14 translates relative to side surface 15. Of course, scraping may also occur during a downward movement of piston 2 from TDC to BDC.
  • cuff-ring 12 may heat up, for example, due to friction. Also, thermal heat produced during operation of internal combustion engine 1 may cause cuff-ring 12 to heat up over time. Thus, cuff-ring 12 may expand during operation of internal combustion engine 1. If, as disclosed herein, cuff-ring 12 is position with its top end 17 at only a small clearance distance away from cylinder head 4, thermal expansion of cuff-ring 12 within liner recess 10 may cause cuff-ring 12 to contact cylinder head 4 with its top end 17.
  • the contact surface between cuff-ring 12 and cylinder head 4 is mainly defined by an area of top end 17 contacting cylinder head 4. Due to the contact between cuff-ring 12 and cylinder head 4, via top end 17, a compression force is exerted onto cuff-ring 12, which may cause cuff-ring 12 to deform. This, in turn, may have an adverse effect on the upward and/or downward movement of piston 2, which is why deformation of cuff-ring 12 due to a contact of cuff-ring 12 with cylinder head 4 should be avoided or at least reduced.
  • the contact surface between cuff-ring 12 and cylinder head 4 may be reduced, by forming cuff-ring 12 with protrusions 18 and/or recesses 25, as exemplary shown in Fig. 1 to 7 .
  • a contact surface between cuff-ring 12 and cylinder head 4 is reduced to an area defined by distal end 19 of protrusion 18. Because the area defined by distal end 19 during a potential contact with cylinder head 4 is smaller than an area defined by top end 17 during a potential contact with cylinder head 4, the compression force exerted onto cuff-ring 12 by cylinder head 4 is reduced. Thus, also a potential deformation of cuff-ring 12 due to a contact with cylinder head 4 is reduced.
  • top end 17 no longer is planar but defines a plurality of distal ends 19.
  • the plurality of distal ends 19 contacting cylinder head 4 define a contact surface that is smaller than a contact surface of top end 17 without a recess formed thereon. Consequently, a compression force exerted onto cuff-ring 12 is reduced and a material deformation is reduced as well.
  • protrusion 18 and/or recess 25 are formed such that during a potential contact between cuff-ring 12 and cylinder head 4, the contact is reduced to a line contact, thereby minimizing the contact surface and thus the compression force exerted onto cuff-ring 12.
  • protrusion 18 may comprise distal end 19 formed as a tip.
  • recess 25 shown in Fig. 7 in a way that recess 25 extends in radial direction almost entirely towards circumferential inner and outer sides 14, 13, thereby reducing the plurality of distal ends 19 to tips.
  • distal end 19 may comprise a recess similar to Fig. 7 , thereby reducing the contact surface defined by distal end 19 during a potential contact with cylinder head 4 further.
  • top end 17 with combinations of protrusions and/or recesses are also possible.
  • convex is used to indicate that material is extending outward when viewed in the direction of cuff-ring axis A from bottom end 23 to top end 17 of cuff-ring 12.
  • concave is used to indicate that material is extending inward when viewed in the direction of cuff-ring axis A from bottom end 23 to top end 17 of cuff-ring 12.

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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)
EP15150637.5A 2015-01-09 2015-01-09 Insert annulaire pour chemise de cylindre Active EP3043054B1 (fr)

Priority Applications (1)

Application Number Priority Date Filing Date Title
EP15150637.5A EP3043054B1 (fr) 2015-01-09 2015-01-09 Insert annulaire pour chemise de cylindre

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
EP15150637.5A EP3043054B1 (fr) 2015-01-09 2015-01-09 Insert annulaire pour chemise de cylindre

Publications (2)

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EP3043054A1 true EP3043054A1 (fr) 2016-07-13
EP3043054B1 EP3043054B1 (fr) 2019-05-01

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
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
EP3670882A1 (fr) * 2018-12-18 2020-06-24 FPT Motorenforschung AG Moteur diesel à combustion interne
DE102021128654A1 (de) 2020-11-12 2022-05-12 Caterpillar Inc. Kolben mit geglätteter äusserer kronenoberfläche in ablagerungsempfindlicher zone

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP4143463A1 (fr) 2020-04-30 2023-03-08 Wärtsilä Finland Oy Bague anti-polissage

Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE886545C (de) * 1944-05-08 1953-08-13 Sulzer Ag Brennkraftmaschine
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
US6164260A (en) 1999-07-13 2000-12-26 Caterpillar Inc. Scraping ring and sealing ring used with a cylinder liner in an internal combustion engine
DE10121852A1 (de) * 2001-05-04 2002-11-14 Man B & W Diesel Ag Hubkolbenbrennkraftmaschine
US20120240883A1 (en) * 2011-03-21 2012-09-27 Cummins Intellectual Property, Inc. Internal combustion engine having improved cooling arrangement

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
DE886545C (de) * 1944-05-08 1953-08-13 Sulzer Ag Brennkraftmaschine
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
US6164260A (en) 1999-07-13 2000-12-26 Caterpillar Inc. Scraping ring and sealing ring used with a cylinder liner in an internal combustion engine
DE10121852A1 (de) * 2001-05-04 2002-11-14 Man B & W Diesel Ag Hubkolbenbrennkraftmaschine
US20120240883A1 (en) * 2011-03-21 2012-09-27 Cummins Intellectual Property, Inc. Internal combustion engine having improved cooling arrangement

Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3670882A1 (fr) * 2018-12-18 2020-06-24 FPT Motorenforschung AG Moteur diesel à combustion interne
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
DE102021128654A1 (de) 2020-11-12 2022-05-12 Caterpillar Inc. Kolben mit geglätteter äusserer kronenoberfläche in ablagerungsempfindlicher zone
US11346301B1 (en) 2020-11-12 2022-05-31 Caterpillar Inc. Piston having smoothed outer crown surface in deposit-sensitive zone

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