EP4208656A1 - Système de segment de piston pour un moteur à combustion interne à injection directe d'eau - Google Patents

Système de segment de piston pour un moteur à combustion interne à injection directe d'eau

Info

Publication number
EP4208656A1
EP4208656A1 EP21751813.3A EP21751813A EP4208656A1 EP 4208656 A1 EP4208656 A1 EP 4208656A1 EP 21751813 A EP21751813 A EP 21751813A EP 4208656 A1 EP4208656 A1 EP 4208656A1
Authority
EP
European Patent Office
Prior art keywords
piston ring
ring
oil
contact area
compression
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.)
Pending
Application number
EP21751813.3A
Other languages
German (de)
English (en)
Inventor
Richard Mittler
Fabian RUCH
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.)
Federal Mogul Burscheid GmbH
Original Assignee
Federal Mogul Burscheid GmbH
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 Federal Mogul Burscheid GmbH filed Critical Federal Mogul Burscheid GmbH
Publication of EP4208656A1 publication Critical patent/EP4208656A1/fr
Pending legal-status Critical Current

Links

Classifications

    • 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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/10—Special members for adjusting the rings
    • 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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • 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
    • F16J1/00—Pistons; Trunk pistons; Plungers
    • 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
    • F16J9/00—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction
    • F16J9/06—Piston-rings, e.g. non-metallic piston-rings, seats therefor; Ring sealings of similar construction using separate springs or elastic elements expanding the rings; Springs therefor ; Expansion by wedging
    • F16J9/064—Rings with a flat annular side rail
    • F16J9/066—Spring expander from sheet metal
    • F16J9/068—Spring expander from sheet metal corrugated in the axial direction

Definitions

  • the present invention relates to a piston ring system for an internal combustion engine with direct water injection.
  • Piston rings for internal combustion engines must meet all the requirements for dynamic sealing. They have to withstand both thermal and chemical influences by preventing the passage of gas from the combustion chamber into the crankcase so that no gas pressure or engine performance is lost. In addition, they should prevent the passage of oil from the crankcase into the combustion chamber, distribute the oil on the cylinder wall and ensure a precisely defined oil film thickness on the cylinder wall. Other tasks of the piston rings are stabilization of the piston movement, heat transfer (heat dissipation) from the piston to the cylinder. To long service life, operational reliability and cost-effectiveness over the entire
  • piston rings should have low frictional resistance and good resistance and wear resistance to thermomechanical fatigue, chemical attack and hot corrosion.
  • Piston rings are advantageously arranged in the piston for specific requirements. Such systems have the main tasks of sealing combustion gases,
  • Direct water injection means that water is injected directly into the cylinder for cooling in order to reduce the rising temperature in the combustion tract as the compression ratio increases. This prevents harmful engine knocking and increases compression and boost pressure.
  • direct water injection can weaken or even tear the oil film, resulting in insufficient lubrication.
  • the object of the invention is to provide a piston ring system for an internal combustion engine with direct water injection, which supports the distribution of the oil that is present, is not matched to very small amounts of oil, and thus prevents insufficient lubrication.
  • the invention relates to a piston ring system for an internal combustion engine, comprising a first compression piston ring, a second compression piston ring, and an oil control piston ring.
  • the first compression piston ring has a first ring body with a first upper ring flank, a first lower ring flank, a first ring inner side, a first ring outer side, and two first abutment surfaces. Furthermore, a first contact area of the first annular body with a cylinder running surface is arranged above a first piston ring center and at least one first oil pocket is arranged below the first contact area in the circumferential direction.
  • the second compression piston ring includes a second ring body with a second upper ring flank, a second lower ring flank, a second ring inner side, a second ring outer side, and two second abutment surfaces. Furthermore, a second
  • the oil control piston ring is designed in one piece, in two pieces or in three pieces.
  • the advantage of the piston ring system according to the invention is that the distribution of the existing oil is supported and this is not tailored to very small amounts of oil. This means that the oil film is not weakened or cracked despite direct water injection into the piston, and insufficient lubrication does not occur.
  • a main contour of the compression piston rings describes a continuous curve that connects the offset first oil pocket upper edge with the first contact area at a constant tangent in order to ensure the hydrodynamic bearing portion over the entire running surface of the compression piston rings.
  • the first contact area of the ring body is at 1-40%, preferably 5-20% of the axial height of the upper outlet of the groove.
  • the second contact area of the ring body is at 1-40%, preferably 5-20% of the axial height of the upper outlet of the groove.
  • the first contact area of the first ring body with the cylinder running surface is arranged above the first piston ring center, preferably at a height of 75 to 95%, particularly preferably at a height of 80 to 90%.
  • the stated height of the first ring body is measured from the first lower ring flank.
  • the overall height of the first ring body corresponds to the greatest distance between the first upper ring flank and the first lower ring flank, measured in the axial direction.
  • the contact area of the second ring body with the cylinder running surface is arranged above the middle of the second piston ring, preferably at a height of 75 to 95%, particularly preferably at a height of 80 to 90%.
  • the stated height of the second ring body is measured from the second lower ring flank.
  • the overall height of the second ring body corresponds to the greatest distance between the second upper ring flank and the second lower ring flank, measured in the axial direction.
  • the second contact area of the second ring body with the cylinder running surface is arranged below the middle of the second piston ring, preferably at a height of 25-45%, particularly preferably at a height of
  • An arrangement of the second contact area of the second ring body with the Cylinder running surface below the middle of the second piston ring ensures that the piston ring is pushed away from the cylinder wall more strongly by the oil during the compression stroke and exhaust stroke of a four-stroke engine or during compression / intake of a two-stroke engine and less oil is scraped off.
  • the first compression piston ring and the second compression piston ring have the same dimensions and cross sections.
  • a cross-sectional plane is spanned by an axis in the axial direction of the piston or piston ring and an axis in the radial direction.
  • the same dimensions and cross-sections of the first and second compression piston rings simplify production and also reduce costs.
  • the at least one first oil pocket is divided into a number of sections in the circumferential direction. This ensures that the oil is stored or distributed evenly without the oil flowing in a circumferential direction.
  • the at least one first oil pocket is divided into 20 to 30 sections.
  • the at least one second oil pocket is divided into a number of sections in the circumferential direction. This ensures that the oil is stored or distributed evenly without the oil flowing in a circumferential direction. Mass flow consistency also creates a vortex in the oil pocket on the power stroke of a two-stroke engine, or on the intake and power strokes of a four-stroke engine, to disrupt hydrodynamic oil flow at high piston speeds.
  • the at least one second oil pocket is divided into 20 to 30 sections.
  • a radius of curvature of a running surface profile in the area of the first contact area corresponds to 2.5 to 5% of the value of the piston ring height in cross section.
  • a radius of curvature of a running surface profile in the area of the second contact area is smaller in cross section than the radius of curvature of the first contact area. Since the radius of curvature of a tread profile, viewed in cross-section of the second ring body, in the area of the second contact area is smaller than the radius of curvature of the first contact area, the second compression piston ring can assist in oil scraping in order to provide an optimal amount of oil for the first compression piston ring.
  • the ratio of the radial distance from a bottom of the first oil pocket to the first contact area and the radial distance from the bottom of the first oil pocket to a first oil pocket top edge offset in the radial direction is between 1.5 and 3 in the cross section of the first ring body , preferably between 2 and 2.5.
  • the advantage of this geometry relates to the tribological properties of the surfaces of the piston ring and cylinder that are in relative motion to one another. Optimal flow into the oil pocket, flow out of the oil pocket and storage of the oil in it form an oil film which, despite direct water injection, is sufficiently thick and does not tear.
  • the ratio of the radial distance from a bottom of the second oil pocket to the second contact area and the radial distance from a bottom of the second oil pocket to a second oil pocket top edge offset in the radial direction is between 1.5 and 4 in the cross section of the second ring body .5, preferably between 2.5 and 3.5. This geometry is advantageous in terms of friction,
  • the tread profile has reduced oil flow thanks to an optimized profile, on which carbon can only be deposited with difficulty during the compression stroke and exhaust stroke of a four-stroke engine or during the compression/intake of a two-stroke engine. It is preferred that the first compression piston ring is arranged on the combustion chamber side
  • Oil control piston ring is arranged on the crankcase side, and the second compression piston ring is arranged between the first compression piston ring and the oil control piston ring. Further, it is preferable that a first land height separates an installation space of the first compression piston ring and an installation space of the second compression piston ring in the axial direction, and a second land height separates the installation space of the second compression piston ring and an installation space of the oil control piston ring in the axial direction.
  • FIG. 1 shows a piston ring system according to an embodiment of the invention
  • FIG. 2 shows a compression piston ring main contour.
  • FIG. 1 shows a cross-sectional view of a piston ring system.
  • 3 grooves are arranged in a piston, with a first compression piston ring 2 being arranged in the uppermost groove, a second compression piston ring 4 being arranged in the middle groove and an oil scraper piston ring 6 being arranged in the lower groove, which is below the other rings, namely at a distance of the second land height 90 is arranged.
  • the main task of the compression piston rings 2, 4 is to prevent the passage of combustion gases between the piston and the cylinder wall into the crankcase.
  • the main task of the oil control piston ring 6 is to seal between the crankcase and combustion housing and to regulate the oil film.
  • the first compression piston ring 2 has a first ring body 8 with a first upper ring flank 10 , a first lower ring flank 12 , a first ring inner side 14 and a first ring outer side 16 .
  • a first contact area 18 of the first ring body 8 with a cylinder running surface 20 is arranged above a first piston ring center 22 .
  • a first oil pocket 24 for storing oil is arranged below the first contact area 18, this supporting the regulation of the oil film on the cylinder running surface.
  • the first contact area 18 is further away from a base of the upper piston groove in the radial direction than a first upper edge 42 of the groove.
  • the second compression piston ring 4 is located below the first ring at a distance of the first land height 89 and has a second ring body 26 with a second upper ring flank 28, a second lower ring flank 30, a second ring inner side 32 and a second ring outer side 34.
  • Ring body 26 with the cylinder surface 20 is arranged above a second piston ring center 22, but can also be arranged below a second piston ring center 22.
  • a second oil pocket 40 for storing oil is arranged below the second contact area 36, this supporting the regulation of the oil film on the cylinder running surface.
  • the second contact area 36 is further away from a base of the central piston groove in the radial direction than a second upper edge 44.
  • the oil scraper ring is in three parts, but can also be in two parts, and has two lamellae that are pressed against the cylinder wall by a spacer and expander spring.
  • the overall height of the first ring body corresponds to the greatest distance between the first upper ring flank and the first lower ring flank, measured in the axial direction.
  • FIG. 2 shows a compression piston ring master contour that describes a smooth curve that connects the offset first oil pocket top edge 42 to the first contact region 18 in a tangent-continuous manner.

Landscapes

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

Abstract

L'invention concerne un système de segment de piston conçu pour un moteur à combustion interne, qui comprend un premier segment de compression (2), un deuxième segment de compression (4), et un segment racleur d'huile (6). Le premier segment de compression (2) présente un premier corps de segment (8) avec un premier flanc de segment supérieur (10), un premier flanc de segment inférieur (12), une première face intérieure de segment (14), une première face extérieure de segment (16), et deux premières surfaces de butée, et une surface de roulement de cylindre (20) d'une première région de contact (18) du premier corps de segment (8) est disposée au-dessus d'un premier centre de segment de piston (22), au moins une première poche d'huile (24) étant disposée sous la première région de contact (18) dans la direction circonférentielle ; et le deuxième segment de compression (4) comprend un deuxième corps de segment (26) avec un deuxième flanc de segment supérieur (28), un deuxième flanc de segment inférieur (30), une deuxième face intérieure de segment (32), une deuxième face extérieure de segment (34), et deux deuxièmes surfaces de butée, et une surface de roulement de cylindre (20) d'une deuxième région de contact (36) du deuxième corps de segment (26) étant disposée au-dessus ou au-dessous d'un deuxième centre de segment de piston (38), au moins une deuxième poche d'huile (40) étant disposée sous la deuxième région de contact (36) dans la direction circonférentielle, le segment racleur d'huile (6) se présentant sous forme de segment racleur d'huile en deux ou trois parties.
EP21751813.3A 2020-09-01 2021-07-29 Système de segment de piston pour un moteur à combustion interne à injection directe d'eau Pending EP4208656A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102020122862.7A DE102020122862A1 (de) 2020-09-01 2020-09-01 Kolbenringsystem für einen verbrennungsmotor mit wasserdirekteinspritzung
PCT/EP2021/071278 WO2022048832A1 (fr) 2020-09-01 2021-07-29 Système de segment de piston pour un moteur à combustion interne à injection directe d'eau

Publications (1)

Publication Number Publication Date
EP4208656A1 true EP4208656A1 (fr) 2023-07-12

Family

ID=77249836

Family Applications (1)

Application Number Title Priority Date Filing Date
EP21751813.3A Pending EP4208656A1 (fr) 2020-09-01 2021-07-29 Système de segment de piston pour un moteur à combustion interne à injection directe d'eau

Country Status (4)

Country Link
US (1) US11959552B2 (fr)
EP (1) EP4208656A1 (fr)
DE (1) DE102020122862A1 (fr)
WO (1) WO2022048832A1 (fr)

Family Cites Families (11)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US1585422A (en) 1922-11-22 1926-05-18 Henry R Seifert Piston ring
US1560307A (en) * 1925-07-08 1925-11-03 Dock J Peeler Piston
US3095204A (en) * 1961-03-08 1963-06-25 California Research Corp Wear-resistant lining for piston-ring groove
JP3216000B2 (ja) 1995-06-20 2001-10-09 株式会社クボタ エンジンの圧力リング
US20080017162A1 (en) * 2006-07-24 2008-01-24 Clever Glenn E Surface treated compression ring and method of manufacture
DE102009036240B4 (de) 2009-08-05 2014-11-13 Federal-Mogul Burscheid Gmbh Kompressionskolbenring
EP2284422B1 (fr) * 2009-08-12 2012-11-07 Doosan Infracore Co., Ltd. Piston pour moteur disposant d'un comportement stable de segment de piston
JP2014101893A (ja) 2012-11-16 2014-06-05 Toyota Central R&D Labs Inc 圧力リング装着ピストン
US10113643B2 (en) * 2014-03-18 2018-10-30 Ford Global Technologies, Llc Compression piston ring for an internal combustion engine
DE102015111306B3 (de) 2015-07-13 2016-07-14 Federal-Mogul Burscheid Gmbh Kompressionskolbenring mit Profilierung
DE102016110105B4 (de) 2016-06-01 2018-08-02 Federal-Mogul Burscheid Gmbh Kompressions-Ölabstreif-Kolbenring

Also Published As

Publication number Publication date
US20230272853A1 (en) 2023-08-31
US11959552B2 (en) 2024-04-16
DE102020122862A1 (de) 2022-03-03
WO2022048832A1 (fr) 2022-03-10

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