EP3583308A1 - Cylindre d'un moteur à combustion interne - Google Patents

Cylindre d'un moteur à combustion interne

Info

Publication number
EP3583308A1
EP3583308A1 EP18710997.0A EP18710997A EP3583308A1 EP 3583308 A1 EP3583308 A1 EP 3583308A1 EP 18710997 A EP18710997 A EP 18710997A EP 3583308 A1 EP3583308 A1 EP 3583308A1
Authority
EP
European Patent Office
Prior art keywords
ring
groove
piston ring
cylinder
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.)
Withdrawn
Application number
EP18710997.0A
Other languages
German (de)
English (en)
Inventor
Talat Shaer
Marcel Morgenstern
Markus Bauer
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.)
MAN Energy Solutions SE
Original Assignee
MAN Energy Solutions SE
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 Energy Solutions SE filed Critical MAN Energy Solutions SE
Publication of EP3583308A1 publication Critical patent/EP3583308A1/fr
Withdrawn legal-status Critical Current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
    • F16J9/06—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
    • 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
    • F02F3/00—Pistons 
    • 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
    • F02F5/00—Piston rings, e.g. associated with piston crown
    • 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
    • F16J9/061—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 using metallic coiled or blade springs
    • F16J9/062—Coiled spring along the entire circumference
    • 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
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping 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
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings
    • F16J9/203—Oil-scraping 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
    • F16J9/12—Details
    • F16J9/20—Rings with special cross-section; Oil-scraping rings
    • F16J9/206—One-piece oil-scraping 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
    • F16J9/12—Details
    • F16J9/22—Rings for preventing wear of grooves or like seatings
    • 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
    • F16J9/061—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 using metallic coiled or blade springs
    • F16J9/063—Strip or wire along the entire circumference

Definitions

  • the invention relates to a cylinder of a Brennkraftmasehine according to the preamble of Anspaichs first
  • Internal combustion engines typically have several cylinders. Each cylinder of an internal combustion engine has a cylinder caliber which is guided in a cylinder bore of the cylinder. During a work cycle, the Zy-Andres piston in the cylinder liner of the respective cylinder is movable up and down.
  • the cylinder piston abuts with a radially outer surface of the cylinder piston against a radially inner surface of the Zyiinderiaufbuchse. Between these surfaces a running gap is defined.
  • the Zyiinderkolben has on its radially outer surface a plurality of annular grooves which are bounded by ring lands and separated from each other, said annular grooves receiving piston rings which protrude into the formed between the radially outer surface of the cylinder piston and the radially inner surface of the Zyiin- derutzbuchse Laufspalf.
  • Each of the annular grooves takes on either a compression ring designed as a piston ring or as a piston ring, which rests with a radially outer piston ring portion on the radially inner surface of the cylinder liner.
  • a piston ring formed as Verdagtungsring serves the gas-tight seal of the running gap between the cylinder piston and the Zyiinderiaufbuchse.
  • a piston ring formed as an oil scraper ring serves to scrape off oil from the radially inner race of the cylinder liner to prevent excess oil from entering the combustion chamber of the respective cylinder via the raceway.
  • This lifting of the compression rings from the lower groove flanks of the annular grooves is determined by the forces acting on the respective piston ring during operation. From practice it is known to adjust a force acting on the respective piston ring force equilibrium; which is responsible for the lifting of the piston ring from the lower groove flank of the respective annular groove. to open the respective piston ring at a devisssosite by forming a gap, wherein the size of this gap determines the force acting on the piston ring force equilibrium. There is a need to axially relieve at least the compression rings of a cylinder of an internal combustion engine in order to reduce a force which is required for lifting the respective compression ring from the lower groove groove of the respective annular groove.
  • the present invention has the object to provide a novel cylinder of an internal combustion engine.
  • This object is achieved by a cylinder according to claim 1.
  • a cylinder according to claim 1 in the lower groove flank of at least one or each formed as a compressor ring piston ring receiving annular groove and / or in the lower ring flank of at least one or each formed as a compressor ring piston ring recess, Such depressions in the region of the lower groove flank of an annular groove and / or the lower ring edge of a piston ring, the respective piston ring can be relieved axially.
  • the respective recess runs in the circumferential direction, this development is particularly preferred for the axial relief of the respective piston ring.
  • the respective recess has a radial width which is 0.05 times and is the radial depth of the respective annular groove 0.05 and / or an axial depth which is greater than zero and is smaller than an axial thickness of the respective piston ring.
  • a distance between a radial center of the depression and the ring back of the individual piston ring is preferably greater than zero and less than a radial thickness of the respective piston ring minus 0.5 mm.
  • a distance between a radially outer end of the recess and a radially outer end of the respective annular groove is preferably greater than zero. This dimensioning of the respective depression is particularly preferred and ensures an advantageous pressure equalization between the upper annular flank and the lower annular flank of the respective piston ring so as to facilitate the lifting of the piston ring from the lower groove flank.
  • the respective piston ring has at least one channel, which has the respective depression with a chamber between the upper groove flank of the respective annular groove and the upper flank of the respective piston ring or with a chamber between the groove bottom of the respective annular groove and the Ring back of each piston ring coupled.
  • FIG. 1 a a detail of FIG. 1:
  • FIG. 2 shows a schematic cross section through a second Zyiinder invention
  • Fig. 2a a detail of Fig. 2;
  • FIG. 3 shows a schematic cross section through a third cylinder according to the invention
  • FIG. 4 shows a schematic cross section through a fourth cylinder according to the invention
  • FIG. 5 shows a schematic cross section through a fifth cylinder according to the invention
  • FIG. 8 shows a schematic cross section through a further cylinder according to the invention.
  • the invention relates to a cylinder of an internal combustion engine.
  • 1 shows a schematic cross section through a cylinder 10 of an internal combustion engine, FIG. 1 showing a cylinder liner 11 from the cylinder 10 and a cylinder barrel 12 guided in the cylinder liner 11.
  • the cylinder drums 12 are movable up and down during operation of the respective cylinder 10 in the cylinder bushing 11 during operation of the internal combustion engine or cylinder 10.
  • a so-called Kolbenheden 13 of the cylinder piston 12 defines a combustion chamber 14 of the respective cylinder 10 in sections.
  • the cylinder piston 12 has a radially outer surface 15 which defines a running gap 17 with a radially inner running surface 18 of the Zyfinder liner 1 1!
  • This Laufspait 17 for the cylinder 12 must be sealed gas-tight on the one hand, on the other hand must be avoided that passes through this Laufspait 17 Qi In the combustion chamber 14 of the cylinder.
  • annular grooves 18 are introduced, which are spaced apart from each other by annular webs 19 and from each other.
  • Each annular groove 18 accommodates a piston ring 20, that is to say a piston ring 20 designed as a compression ring 21 or a piston ring 20 formed as oil ring 22.
  • compressor rings 21 and a lower annular groove 18 are respectively provided in two upper annular grooves IS ⁇ iabsireifring 22 added.
  • Each annular groove 18 is bounded by an upper groove flank 23, a lower groove flank 24 and radially ' inside 0urch a groove bottom 25.
  • piston ring 20 Each received in an annular groove 18 piston ring 20 is äurch an upper annular edge 26, a lower annular edge 27, a ring back 28 and the ring back 28 opposite section 29 limited !.
  • the upper annular edge 26 of the piston ring 20 is the upper groove edge 23 of the respective annular groove 18 opposite.
  • the lower ring flank 2? of the respective piston ring 20 is the lower groove edge 24 of the respective annular groove 18 opposite.
  • the ring back 28 of the respective piston ring 20 is the respective groove bottom 25 of the respective annular groove 18 opposite. With the ring back 28 opposite portion 29 of the piston ring 20, which projects into the running gap 20, the respective piston ring 20 comes to the running surface 18 of the Zylindedaufbuchse 11 to the plant.
  • each annular groove 18 has a radial depth X1 and an axial width Y1. Further, FIG. 1a shows the radial direction R and the axial axis ⁇ of the piston 12 to which these dimensions refer.
  • Each piston ring 20 has an axial height Y2 and a radial thickness X2.
  • For the purposes of the present invention is in the lower groove edge 24 at least the or each designed as a compressor ring 21 piston ring 20 receiving annular groove 18 and / or in the lower ring edge 2? at least the or each formed as a compressor ring 21 piston ring 20 has a recess 30 and 31, respectively.
  • the recesses 30, 31 are circumferentially performed circumferentially.
  • the recesses 30, 31 it is also possible for the recesses 30, 31 to be interrupted at defined circumferential positions.
  • the respective recess 30, 31 has a radial width X3 and an axial depth Y3.
  • the axial width X3 of the respective indentation 30, 31 is between 0.05 times and 0.09 times the radial depth XI of the respective annular groove 18.
  • the radial width X3 of the respective recess 30, 31 is between 0, 1-fold and 0.5-fold, more preferably between 0.25-fell and the ö ; 35 ⁇ fold, the radial depth X1 of the respective annular groove 18th
  • the axial depth Y3 of the respective recess 30, 31 is greater than zero and smaller than the axial thickness Y2 of the respective piston ring 20.
  • this axial depth Y3 of the respective recess 30, 31 between 0.1 mm and 1, 0 mm, especially preferably between 0.3 mm and QJ mm.
  • the axial depth Y3 of the respective recess 30, 31 is at least 0.01 mm, preferably at least 0.05 mm.
  • the respective recess 30, 31 is further characterized by a distance X4 whose radial center to the ring back 28 of the respective piston ring 20 and by the distance X5 between the radially outer end of the respective recess 30, 31 and the radially outer end of the respective annular groove 13.
  • the distance X4 between the radial center of the respective recess 30, 31 and the ring back 28 of the respective piston ring 20 is greater than zero and smaller than the radial thickness X2 of the respective piston ring minus 0.5 mm.
  • this distance X4 between the radial center of the respective recess 30, 31 and the ring back of the respective piston ring 20 is between 0.3 times and GJ times, more preferably between 0.45 times and 0.55 times times the radial thickness X2 of the respective piston ring.
  • the distance X5 between the radially outer end of the respective recess 30, 31 and the radially outer end of the respective annular groove 18 is greater than zero, preferably greater than 0.05 mm, more preferably greater than 0.1 mm.
  • a defined pressure equalization between an upper annular flank 26 and a lower annular flank 27 of the respective piston ring 20 can be ensured, a force which during a cycle for lifting the respective piston ring 20 from the respective lower groove flank 24 of the respective piston ring 20 receiving annular groove 18 is required, can be so reliably and easily reduced.
  • the piston rings 20 are slotted at a circumferential position, as is common in the art,
  • a channel 32 is introduced in the piston ring 20, namely in the respective compressor ring 21, a channel 32 is introduced. via which the respective recess 30 is coupled to a chamber which is formed between the upper Ringfianke 26 of the respective piston ring 20 and the upper groove flank 23 of the respective piston ring 20 receiving annular groove 18.
  • Such a channel 32 is introduced into the piston ring 20 at at least one circumferential position, preferably at a plurality of circumferential positions.
  • Fig. 6 shows an embodiment of the invention, in which in the piston rings 20. Namely in the Verdiehterringe 21, also channels 33 are introduced, wherein the channels 33 of FIG.
  • FIGS. 5, 8 couple the respective recess 30 with a chamber, the zwi ⁇ see the Ring back 28 of the respective piston ring 20 and the groove bottom 25 of the respective piston ring 20 receiving annular groove 18 is formed. 5 and 8, the pressure equalization between the upper ring edge and the lower Ringfianke the respective piston ring 20 can be easily and reliably provided.
  • the channels of Fig. 5, 8 can also be used in the embodiments of FIGS. 2 to 4, wherein in the embodiments of FIGS. 2 to 4 kooimuniziren such channels, in particular with the recesses 31 in compressor rings 21.

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 cylindre (10) d'un moteur à combustion interne. Le cylindre comprend une chemise (11) et un piston (12) guidé dans la chemise (11) du cylindre. Le piston (12) du cylindre comprend plusieurs rainures (18) annulaires délimitées par des nervures (19) annulaires et des rainures (18) annulaires séparées les unes des autres par les nervures (19) annulaires. Chacune des rainures (18) annulaires loge un segment (20) de piston réalisé sous la forme d'un segment racleur (21) ou sous la forme d'un segment racleur d'huile (22). Chaque rainure (20) annulaire du segment est délimitée par un flanc supérieur (23), un flanc inférieur (24) et un fond (25), et chaque segment (20) de piston présente un flanc inférieur (27) tourné vers le flanc inférieur (24) de la rainure (18) annulaire respective, un flanc supérieur (26) tourné vers le flanc supérieur (23) de la rainure (18) annulaire respective, un dos (28) tourné vers le fond (25) de la rainure (18) annulaire respective et une partie (29) opposée au dos (28) annulaire et s'appliquant contre une surface de roulement (18) radialement intérieure de la chemise (11) du cylindre, et un évidement (30) est ménagé dans le flanc inférieur (24) au moins de la ou de chaque rainure (18) annulaire logeant un segment (20) de piston réalisé sous la forme d'un segment racleur (21) et/ou dans le flanc inférieur (27) au moins du ou de chaque segment (20) de piston réalisé sous la forme d'un segment racleur (21).
EP18710997.0A 2017-02-16 2018-02-02 Cylindre d'un moteur à combustion interne Withdrawn EP3583308A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
DE102017103159.6A DE102017103159B4 (de) 2017-02-16 2017-02-16 Zylinder einer Brennkraftmaschine
PCT/DE2018/100085 WO2018149444A1 (fr) 2017-02-16 2018-02-02 Cylindre d'un moteur à combustion interne

Publications (1)

Publication Number Publication Date
EP3583308A1 true EP3583308A1 (fr) 2019-12-25

Family

ID=61628085

Family Applications (1)

Application Number Title Priority Date Filing Date
EP18710997.0A Withdrawn EP3583308A1 (fr) 2017-02-16 2018-02-02 Cylindre d'un moteur à combustion interne

Country Status (8)

Country Link
US (1) US11982357B2 (fr)
EP (1) EP3583308A1 (fr)
JP (1) JP6852173B2 (fr)
KR (1) KR20190108630A (fr)
CN (1) CN110312858A (fr)
CA (1) CA3053653C (fr)
DE (1) DE102017103159B4 (fr)
WO (1) WO2018149444A1 (fr)

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GB2540210B (en) * 2015-07-10 2019-02-06 Ford Global Tech Llc Piston ring configured to reduce friction

Also Published As

Publication number Publication date
US20210381597A1 (en) 2021-12-09
KR20190108630A (ko) 2019-09-24
JP6852173B2 (ja) 2021-03-31
DE102017103159A1 (de) 2018-08-16
JP2020507710A (ja) 2020-03-12
CA3053653C (fr) 2022-06-21
CA3053653A1 (fr) 2018-08-23
US11982357B2 (en) 2024-05-14
DE102017103159B4 (de) 2023-02-02
WO2018149444A1 (fr) 2018-08-23
CN110312858A (zh) 2019-10-08

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