WO2005078268A1 - 内燃機関のピストン装置 - Google Patents
内燃機関のピストン装置 Download PDFInfo
- Publication number
- WO2005078268A1 WO2005078268A1 PCT/JP2005/002041 JP2005002041W WO2005078268A1 WO 2005078268 A1 WO2005078268 A1 WO 2005078268A1 JP 2005002041 W JP2005002041 W JP 2005002041W WO 2005078268 A1 WO2005078268 A1 WO 2005078268A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- piston
- ring
- section
- top land
- internal combustion
- Prior art date
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
- F16J9/12—Details
- F16J9/20—Rings with special cross-section; Oil-scraping rings
-
- 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
- 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
- F16J15/00—Sealings
- F16J15/16—Sealings between relatively-moving surfaces
- F16J15/32—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings
- F16J15/3248—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports
- F16J15/3252—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports
- F16J15/3256—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals
- F16J15/326—Sealings between relatively-moving surfaces with elastic sealings, e.g. O-rings provided with casings or supports with rigid casings or supports comprising two casing or support elements, one attached to each surface, e.g. cartridge or cassette seals with means for detecting or measuring relative rotation of the two elements
Definitions
- the present invention relates to the shape of a piston and a piston ring in an internal combustion engine in which a piston reciprocates.
- the top ring is a gas seal
- the second ring is a gas seal and oil control
- the oil ring is an oil control.Each ring shares the functions of gas seal and oil control. It is a form that satisfies.
- Patent Document 1 Japanese Utility Model Publication No. 58-24558
- Patent Document 2 Japanese Utility Model Application Laid-Open No. 5-42661
- the piston for an internal combustion engine described in Patent Document 2 is designed such that when a compression pressure is applied, the crown surface of the piston body and the upper leg portion of the compression piston ring having a U-shaped cross section come into close contact with each other. Intrusion of the compressed gas into the lock clearance is hindered, and the piston ring cannot be extended sufficiently to the outer peripheral side. Therefore, sufficient gas sealing function and I cannot satisfy the file control function.
- the present invention has been made to solve such a conventional problem, and an object thereof is to provide a piston of an internal combustion engine having a top ring having an excellent gas seal and an oil control function. It is to provide a device.
- a piston device for an internal combustion engine includes a piston body having a ring groove formed by leaving a top land portion on the outer periphery, and an upper leg portion and a lower leg portion connected via a base. And a piston ring having a U-shaped cross section attached to the top land portion.
- the axial width from the boundary between the piston ring base and the upper leg to the lower surface of the lower leg is defined by the axial force from the upper surface of the top land of the piston body to the lower surface of the ring groove where the lower leg is mounted. It is larger than the width.
- another piston device for an internal combustion engine includes a piston main body having a ring groove formed by leaving a top land portion on the outer periphery, and an upper leg portion and a lower leg portion via a base. And a piston ring having a U-shaped cross section attached to the top land portion, and a groove is provided on the thrust side of the top land portion of the piston body.
- Still another aspect of the piston device for an internal combustion engine is that an upper leg portion and a lower leg portion are connected via a base to a piston main body having a ring groove formed by leaving a top land portion on an outer periphery. And a piston ring having a U-shaped cross section attached to the top land portion, and a V-shaped annular groove is provided in a second land portion of the piston body.
- the piston ring may have an upper outer periphery having a BF shape and a lower outer periphery having a straight or tapered contact surface.
- a single piston ring exerts an excellent gas sealing function and an oil control function, so that the number of piston rings can be reduced, and a high rotation speed and high output of an internal combustion engine can be achieved. And low friction can be achieved.
- FIG. 1 is a perspective view showing a piston device 1 of an internal combustion engine according to one embodiment of the present invention.
- FIG. 2 is an enlarged view showing a main part of FIG. 1.
- FIG. 3 is a top view showing an outline of an engine device to which the piston device 1 of the internal combustion engine in FIG. 1 is applied.
- FIG. 4 is a diagram showing the results of a comparison of the oil consumption between the piston device 1 of the internal combustion engine of FIG. 1 and a conventional device.
- FIG. 5 is an enlarged view of a main part showing a piston device 1A for an internal combustion engine according to another embodiment of the present invention.
- FIG. 6 is an enlarged view of a main part showing a piston device 1B for an internal combustion engine according to another embodiment of the present invention.
- FIG. 7 is an enlarged view of a main part showing a piston device 1C for an internal combustion engine according to another embodiment of the present invention.
- the piston device 1 of the internal combustion engine according to the present embodiment includes a piston body 10 having a ring groove 13 formed on the outer periphery thereof while leaving a top land portion 12, and an upper leg portion 22 and a lower leg portion 23. And a piston ring 20 having a U-shaped cross section and connected to the top land portion 12 through
- the axial width h2 from the boundary P between the base 21 of the U-shaped cross section of the piston ring 20 and the upper leg 22 to the lower surface 23a of the lower leg 23 is lower than the upper surface 12b of the top land 12 from the upper surface 12b.
- the piston ring 20 having a U-shaped cross section and the lower surface 13a of the ring groove 13 are brought into close contact with the force S, and the entire piston ring 20 having a U-shaped cross section is formed. Clearance occurs on the inner peripheral surface.
- the piston ring 20 having a U-shaped cross section protrudes to the outer peripheral side, and the sealing characteristics are improved.
- the value of h2-h3 is preferably 40 ⁇ 20 ⁇ m for a gasoline engine and 100 ⁇ 20 m for a diesel engine.
- the tolerance is set to fall within this dimension range.
- a notch 25 is formed in the crown surface 11 of the piston body 10, and the upper leg 22 of the piston ring 20 having a U-shaped cross section is attached to the notch 25.
- the present invention is not limited to such a configuration.
- the notch 25 is not formed in the piston body 10, and the upper leg 22 of the piston ring 20 having a U-shaped cross section is mounted so as to protrude above the crown surface 11 of the piston body 10. The invention applies.
- the axial width h2 from the boundary P between the base 21 of the U-shaped piston ring 20 and the upper leg 22 to the lower surface 23a of the lower leg 23 is determined by the upper surface of the top land 12 (here, The same effect can be obtained by designing the crown surface 11) to have a larger force than the axial width h3 up to the lower surface 13a of the ring groove 13 in which the lower leg 23 is mounted.
- the piston body 10 preferably has a groove 14 on the thrust side of the top land portion 12.
- the groove 14 is located at 80 °, 90 °, and 100 ° from the front position 31 of the engine 30 to the thrust side, along the top land portion 12 from the crown surface 11 of the piston body 10 to the top land portion 12. It is formed over the outer peripheral surface 12a of the 12.
- a mission 32 communicates with the engine 30.
- the front end of the engine 30 is referred to as a front side, and the rear end is referred to as a rear side.
- the position where the groove 14 is formed is not particularly limited as long as it is on the thrust side (a range of 0 to 180 degrees), but is preferably formed in a range of 45 to 135 degrees.
- the back pressure of the ring can be increased, and the oil control function and the sealing function are improved.
- This configuration requires only the piston device designed so that the lower surface 23a of the lower leg 23 of the piston ring 20 and the lower surface 13a of the ring groove 13 come into close contact with each other when the above-described compression pressure is applied.
- the present invention is also applied to a conventional piston device in which the crown surface of the piston body and the upper leg portion of the piston ring having a U-shaped cross section are brought into close contact with each other, and exhibits an excellent effect.
- the V-shaped shape is a groove shape in which the upper surface side is horizontal or the inner peripheral side is inclined upward and the lower surface side is inclined downward so that the radial width decreases.
- the inclination of the lower surface is the piston shaft. It is preferable that the angle is 15 to 45 degrees.
- the shape of the annular groove include a U-shaped cross section, a U-shaped cross section, and an inverted V-shape.
- the lower surface 23a of the lower leg 23 of the piston ring 20 and the lower surface 13a of the ring groove 13 have a U-shaped cross section. This applies not only to piston devices designed to be in close contact with each other, but also to piston devices that are conventionally designed so that the crown surface of the piston body and the upper leg of the U-shaped piston ring are in close contact with each other. Demonstrates excellent effects.
- the piston body 10 descends on the thrust side during the expansion stroke.
- the dimension tl difference between the top land portion 12 and the second land portion 16
- tl t2 is substantially equal to the dimension t2 (ring plate thickness) in FIG.
- tl t2 is preferably designed to be 0-50 m.
- the piston ring 20 having a U-shaped cross section is slidably mounted on the lower surface 23a of the lower leg 23 on the lower surface 13a of the ring groove 13.
- the lower surface 23a of the lower leg 23 slides along the lower surface 13a of the ring groove 13 so as to protrude, and the inner periphery 21a of the base 21 and the outer periphery of the top land 12 are formed.
- a gap S is formed between the surface and the surface 12a.
- a gap is formed between the entire inner peripheral surface of the piston ring 20 and the piston body 10. Since the gap S has a labyrinth effect, it is difficult to transport oil moving from the second land 16 to the rear through the lower surface of the piston ring 20 to the combustion chamber, and an effect of reducing oil consumption is achieved.
- the piston ring 20 has a shape protruding toward the cylinder C when a gas pressure acts even with a small tension, and can exert a gas sealing function.
- a ring back is provided on the thrust side of the top land portion 12 of the piston body 10.
- Grooves 14 for increasing the pressure are provided at positions 80, 90 and 100 degrees from the front position 31 of the engine 30.
- the back pressure of the piston ring 20 on the thrust side increases through the groove 14 as the in-cylinder pressure (combustion pressure) increases during the expansion stroke on the thrust side where the oil film thickness is large during engine operation.
- the oil film can be more actively thinned and a more excellent oil control function can be exhibited.
- the piston ring 20 is attached to the top land portion 12 located at the upper end of the piston main body 10, the temperature of the crown surface 11 and the top land 12 of the piston main body 10 can be reduced. It becomes possible.
- the U-shaped ring (piston ring 20) used for the measurement has a plate thickness of 0.5 mm, hi size of 2. Omm, al size of 2. Omm, and is made of steel.
- a notch is formed in the crown surface of the piston body for mounting the upper leg of the piston ring having a U-shaped cross section, and the piston ring having the U-shaped cross section is formed below the crown surface.
- a ring groove for mounting the lower leg was provided.
- the axial dimensions of the notch and the ring groove were set to be about 50 ⁇ m larger than the axial dimensions of the upper leg and the lower leg of the U-shaped piston ring.
- the radial dimension of the notch and the ring groove was set to be about 50 / zm larger than the al dimension of the U-shaped piston ring.
- Example 1 is a piston device using the piston body.
- Example 2 is a piston device using the piston body.
- Example 3 is a piston device using this piston body.
- the piston ring having a U-shaped cross section according to the present invention reduces oil consumption and blow noise as compared with the conventional single ring specification.
- the oil consumption was further reduced by providing a groove on the thrust side of the piston body.
- the oil consumption was significantly reduced by providing a V-shaped annular groove in the piston body (Example 3).
- the blow-by amount which was 14. OLZmin in the conventional single-ring specification, was reduced to 12.2 LZmin in Example 3.
- FIG. 5 shows a piston device 1A for an internal combustion engine according to another embodiment of the present invention.
- the upper and lower surfaces 12b and 12c of the top land portion 12 are tapered (reverse keystone shape), and the lower surface 22a of the upper leg and the upper surface 23b of the lower leg of the piston ring 20 having a U-shaped cross section. It is different from the piston device 1 of the internal combustion engine according to the above embodiment in that it is tapered so that the axial width of the leg is increased by directing the outer peripheral side.
- the axial width h2 from the boundary portion P between the base 21 of the U-shaped piston ring 20 and the upper leg portion 22 to the lower leg lower surface 23a is equal to the outer peripheral upper end of the top land 12.
- the A force is also preferably designed to be larger than the axial method width h3 up to the lower surface 13a of the ring groove 13 where the lower leg is mounted.
- the axial width hlO from the inner peripheral lower end Q of the upper leg of the U-shaped cross section of the piston ring 20 to the lower leg lower surface 23a is equal to the inner peripheral upper end B of the top land 12 from the lower leg.
- the shaft groove is designed to be larger than the width hll in the axial direction up to the lower surface 13a of the ring groove 13 in which the portion 23 is mounted.
- the lower surface 23 a of the lower leg 23 projects outward along the lower surface 13 a of the ring groove 13.
- a gap is formed between the entire inner peripheral surface of the piston ring 20 and the outer peripheral surface of the top land portion. Since this gap has a labyrinth effect, it is difficult to carry the oil moving from the second land 16 to the rear surface through the lower surface of the piston ring 20 to the combustion chamber, and the effect of reducing oil consumption is exerted. [0027] Also in the present embodiment, it is needless to say that the same operation and effect as in the above embodiment can be obtained.
- FIG. 6 shows a piston device 1B for an internal combustion engine according to another embodiment of the present invention.
- the upper outer periphery 24 of the piston ring 20 has a BF (barrel face) shape with a projection amount of about 0.5 mm
- the lower outer periphery 25 has a tapered contact surface with a projection amount of about 0.5 mm.
- the piston devices 1 and 1A of the internal combustion engine according to the above embodiments are different.
- the upper outer periphery 24 by forming the upper outer periphery 24 into a barrel face shape, it is effective to prevent scuffing, which is difficult to hit by edges.
- the lower outer periphery 25 is formed as a tapered contact surface, there is an advantage that the oil removing effect in the downward stroke of the piston body 10 is excellent.
- the shape is divided into upper and lower parts by one piston ring, there is an advantage that the actual contact width can be reduced and the surface pressure can be increased with the same tension as compared with the piston ring 20 of FIG. That is, when the surface pressure is high, there is an advantage that the oil can be consumed with good followability of the outer periphery and good oil consumption.
- the lower outer periphery 25 may be a straight-shaped contact surface.
- FIG. 7 shows a piston device 1C for an internal combustion engine according to another embodiment of the present invention.
- the upper outer periphery 24 and the lower outer periphery 25 of the piston ring 20 are formed as half-barrel shaped contact surfaces, and the piston devices 1, 1A, 1
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- 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
Description
Claims
Priority Applications (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
EP05710093A EP1719901A4 (en) | 2004-02-12 | 2005-02-10 | PISTON DEVICE FOR INTERNAL COMBUSTION ENGINE |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2004035357A JP2005226522A (ja) | 2004-02-12 | 2004-02-12 | 内燃機関のピストン装置 |
JP2004-035357 | 2004-02-12 |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2005078268A1 true WO2005078268A1 (ja) | 2005-08-25 |
Family
ID=34857679
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2005/002041 WO2005078268A1 (ja) | 2004-02-12 | 2005-02-10 | 内燃機関のピストン装置 |
Country Status (5)
Country | Link |
---|---|
US (1) | US20070272078A1 (ja) |
EP (1) | EP1719901A4 (ja) |
JP (1) | JP2005226522A (ja) |
TW (1) | TW200530525A (ja) |
WO (1) | WO2005078268A1 (ja) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007016945A1 (de) * | 2007-04-05 | 2008-10-30 | Mahle International Gmbh | Kolben für einen Verbrennungsmotor |
DE102008035697A1 (de) * | 2008-07-30 | 2010-02-18 | Mahle International Gmbh | Kolben für einen Verbrennungsmotor |
Families Citing this family (14)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102005041908A1 (de) * | 2005-09-03 | 2007-03-08 | Ks Kolbenschmidt Gmbh | Kolben mit einer unterhalb einer Ringnut angeordneten umlaufenden radialen Vertiefung |
JP4643547B2 (ja) * | 2006-11-29 | 2011-03-02 | トヨタ自動車株式会社 | 内燃機関のピストン |
US10036471B2 (en) * | 2009-11-18 | 2018-07-31 | Achates Power, Inc. | Ported engine constructions with low-tension compression seals |
CN102384062B (zh) * | 2010-08-30 | 2015-12-16 | 中国计量学院 | 活塞往复式压缩机的全无余隙机型的结构 |
CN102384065B (zh) * | 2010-08-30 | 2015-07-22 | 中国计量学院 | 能降低活塞与气缸之间余隙的半v型活塞环及其加工方法 |
CN102384061A (zh) * | 2010-09-02 | 2012-03-21 | 梁嘉麟 | 能够降低活塞与气缸之间余隙的活塞环结构及其加工方法 |
CN102454576A (zh) * | 2010-10-22 | 2012-05-16 | 梁嘉麟 | 能够降低活塞与气缸之间余隙的半v型活塞环的结构形式 |
CN104847625A (zh) * | 2014-03-18 | 2015-08-19 | 梁嘉麟 | 采用无端隙半v型非金属活塞环的活塞往复式压缩机的全无余隙结构 |
CN103993978A (zh) * | 2014-06-08 | 2014-08-20 | 彭常龙 | 一种空气滤清器密封圈 |
BR112017018453B1 (pt) | 2015-03-10 | 2023-02-14 | Liquidpiston, Inc | Montagem de vedação para vedar um vão entre a superfície axial de um rotor de uma máquina rotativa e o compartimento lateral da máquina |
JPWO2017115711A1 (ja) * | 2015-12-28 | 2018-10-18 | 川崎重工業株式会社 | 内燃機関用ピストン |
US20190093767A1 (en) | 2016-03-10 | 2019-03-28 | Liquidpiston, Inc. | Piston Ring for Reduction of Crevice Volume |
DE102018211361B4 (de) * | 2018-07-10 | 2020-03-05 | Federal-Mogul Nürnberg GmbH | Kolben für einen Verbrennungsmotor |
CN114763775A (zh) * | 2021-01-15 | 2022-07-19 | 强莉莉 | 一种迷宫式密封活塞组件 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JPH0469634U (ja) * | 1990-10-24 | 1992-06-19 | ||
JPH0547615U (ja) * | 1991-11-26 | 1993-06-25 | ヤンマーディーゼル株式会社 | 内燃機関用ピストンリング |
JP2001214805A (ja) * | 2000-01-28 | 2001-08-10 | Nippon Piston Ring Co Ltd | ピストン |
Family Cites Families (9)
Publication number | Priority date | Publication date | Assignee | Title |
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US2074581A (en) * | 1934-01-06 | 1937-03-23 | Robert G Frye | Piston for engines |
US2228495A (en) * | 1937-08-25 | 1941-01-14 | Williams Harrison Graham | Composite piston ring |
US2566603A (en) * | 1947-12-18 | 1951-09-04 | Motor Industry Res Ass | Piston ring |
US2844424A (en) * | 1956-02-20 | 1958-07-22 | Rand Goetze Corp | Piston sealing means |
US3901131A (en) * | 1969-04-14 | 1975-08-26 | Ramsey Corp | Anti-emissions compression piston ring |
US3645174A (en) * | 1970-11-10 | 1972-02-29 | Ramsey Corp | Antiemissions compression piston ring |
DE2828749C2 (de) * | 1978-06-30 | 1983-10-20 | M.A.N. Maschinenfabrik Augsburg-Nürnberg AG, 8500 Nürnberg | Kolben für Brennkraftmaschinen |
DE2933702C2 (de) * | 1979-08-21 | 1981-09-17 | Goetze Ag, 5093 Burscheid | Kolbenring für insbesondere Brennkraftmaschinen |
US6347575B1 (en) * | 1999-06-30 | 2002-02-19 | Benjamin V. Booher | Low emission piston and ring for internal combustion engine |
-
2004
- 2004-02-12 JP JP2004035357A patent/JP2005226522A/ja active Pending
-
2005
- 2005-01-21 US US10/597,745 patent/US20070272078A1/en not_active Abandoned
- 2005-02-03 TW TW094103464A patent/TW200530525A/zh unknown
- 2005-02-10 WO PCT/JP2005/002041 patent/WO2005078268A1/ja active Application Filing
- 2005-02-10 EP EP05710093A patent/EP1719901A4/en not_active Withdrawn
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPH0469634U (ja) * | 1990-10-24 | 1992-06-19 | ||
JPH0547615U (ja) * | 1991-11-26 | 1993-06-25 | ヤンマーディーゼル株式会社 | 内燃機関用ピストンリング |
JP2001214805A (ja) * | 2000-01-28 | 2001-08-10 | Nippon Piston Ring Co Ltd | ピストン |
Non-Patent Citations (1)
Title |
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See also references of EP1719901A4 * |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102007016945A1 (de) * | 2007-04-05 | 2008-10-30 | Mahle International Gmbh | Kolben für einen Verbrennungsmotor |
DE102008035697A1 (de) * | 2008-07-30 | 2010-02-18 | Mahle International Gmbh | Kolben für einen Verbrennungsmotor |
Also Published As
Publication number | Publication date |
---|---|
US20070272078A1 (en) | 2007-11-29 |
JP2005226522A (ja) | 2005-08-25 |
EP1719901A1 (en) | 2006-11-08 |
EP1719901A4 (en) | 2009-09-02 |
TW200530525A (en) | 2005-09-16 |
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