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WO2015129074A1 - ピストンリング及び該ピストンリングを備えるエンジン - Google Patents

ピストンリング及び該ピストンリングを備えるエンジン Download PDF

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Publication number
WO2015129074A1
WO2015129074A1 PCT/JP2014/071441 JP2014071441W WO2015129074A1 WO 2015129074 A1 WO2015129074 A1 WO 2015129074A1 JP 2014071441 W JP2014071441 W JP 2014071441W WO 2015129074 A1 WO2015129074 A1 WO 2015129074A1
Authority
WO
WIPO (PCT)
Prior art keywords
piston ring
tongue
peripheral surface
outer peripheral
communication groove
Prior art date
Application number
PCT/JP2014/071441
Other languages
English (en)
French (fr)
Japanese (ja)
Inventor
西田　英朗
淑郎 佐近
伸朗 佐藤
貴史 音羽
Original Assignee
三菱重工業株式会社
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 三菱重工業株式会社 filed Critical 三菱重工業株式会社
Priority to CN201480073889.4A priority Critical patent/CN105934612A/zh
Priority to KR1020167014342A priority patent/KR101823807B1/ko
Publication of WO2015129074A1 publication Critical patent/WO2015129074A1/ja

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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
    • F16J9/14—Joint-closures
    • 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

Definitions

  • the present invention relates to a piston ring and an engine including the piston ring.
  • the piston ring is installed in a piston ring groove formed on the outer periphery of the piston.
  • the piston ring has elasticity, and has a function of maintaining the pressure in the combustion chamber formed by the piston, the cylinder inner peripheral surface, and the cylinder head by sliding and contacting the inner peripheral surface of the cylinder with an appropriate surface pressure. .
  • the piston ring has a ring shape, but a discontinuous portion called a joint portion is provided in a part of the circumferential direction.
  • a gas tight type abutment as described in Patent Document 1 is composed of a concave portion provided on one end side in the circumferential direction of the piston ring and a convex portion provided on the other end side. It is made to fit so that it may overlap.
  • the piston ring is heated by the combustion gas and becomes hot.
  • the temperature on the inner peripheral side of the piston ring is higher than the temperature on the outer peripheral side.
  • the amount of thermal expansion of the piston ring is larger on the inner peripheral side than on the outer peripheral side, so that the joint portion of the piston ring is thermally deformed so as to expand outward in the radial direction of the piston ring.
  • the present invention has been made in order to solve the above problems, and is a gas tight type piston in which the high-pressure and high-speed blow-off of the combustion gas in the non-overlapping region of the first tongue and the second tongue is suppressed, and the durability is improved.
  • An object is to provide a ring and an engine including the piston ring.
  • the piston ring according to the present invention is: A main body extending along the circumferential direction around the axis; A first tongue portion extending from one end of the main body portion to the other end and having a fitting groove extending radially outward of the main body portion and extending along the circumferential direction on one side in the axial direction.
  • a second tongue portion extending from the other end of the main body portion to the one end and forming a joint portion with the first tongue portion by fitting into the fitting groove;
  • the communication groove is positively provided in advance in at least one of the outer peripheral surface of the first tongue and the outer peripheral surface of the second tongue, so that the combustion gas escapes through the communication groove. It is possible to suppress the high-temperature combustion gas from blowing through at high pressure and high speed in the non-overlapping region. As a result, damage in the non-overlapping region is suppressed, and the durability of the piston ring is improved. Further, by providing the communication groove, the rigidity of at least one of the first tongue portion and the second tongue portion is lowered, and the contact surface pressure of the piston ring with respect to the cylinder inner peripheral surface is made uniform. As a result, uneven wear of the piston ring and the cylinder inner peripheral surface 2a is suppressed, and the durability of the piston ring is improved.
  • the communication groove is provided on both the outer peripheral surface of the first tongue and the outer peripheral surface of the second tongue. According to this configuration, by providing the communication grooves on both the outer peripheral surface of the first tongue and the outer peripheral surface of the second tongue in the non-overlapping region, the high-temperature combustion gas in these two non-overlapping regions High-speed and high-pressure blow-through is suppressed, and damage to the piston ring can be further prevented.
  • the cross section of the communication groove in the radial direction is formed in a semicircular shape. According to this configuration, the cross-sectional shape of the communication groove in the vicinity of the communication groove becomes smooth by making the cross-sectional shape of the communication groove in the cross section orthogonal to the axis line a semicircular shape. As a result, stress concentration in the vicinity of the communication groove is alleviated, and the durability of the piston ring can be improved.
  • the cross-sectional area of the communication groove in the radial direction increases from one side to the other side in the axial direction. According to this configuration, when the combustion gas flows from one side to the other side by increasing the cross-sectional area of the communication groove from one side to the other side in the direction along the axis, The speed of the combustion gas flowing out from the other side of the groove can be reduced. For this reason, when another piston ring is arrange
  • the engine according to the present invention includes any one of the above-described piston rings. According to this configuration, in the piston ring, the high-pressure and high-speed blow-off of the combustion gas in the non-overlapping region of the first tongue and the second tongue is suppressed, and the durability of the piston ring is improved. Engine durability is also improved.
  • the cross-sectional area of the communication groove in the radial direction is configured to increase from the combustion chamber side of the engine toward the crank chamber side in the axial direction. According to this configuration, when the combustion gas is about to flow from the combustion chamber side toward the crank chamber side, the speed of the combustion gas flowing out from the crank chamber side of the communication groove can be reduced. For this reason, when the other piston ring is arrange
  • a gas tight type piston ring in which the high-pressure and high-speed blow-off of the combustion gas in the non-overlapping region between the first tongue and the second tongue is suppressed, and the durability is improved.
  • An engine is provided.
  • FIG. 1 is a schematic cross-sectional view of an engine to which a piston ring according to the present invention is applied. It is a perspective view showing the outline appearance of the piston ring concerning a 1st embodiment of the present invention.
  • FIG. 3 is a plan view schematically showing an enlarged region A of FIG. 2 together with a part of a cylinder.
  • FIG. 3 is a perspective view schematically showing an enlarged area A in FIG. 2.
  • FIG. 4 of the piston ring which concerns on 2nd Embodiment of this invention.
  • FIG. 4 of the piston ring which concerns on 3rd Embodiment of this invention.
  • FIG. 4 of the piston ring which concerns on 4th Embodiment of this invention.
  • FIG. 1 is a cross-sectional view schematically showing a configuration of an engine 1 to which a piston ring 10 according to a first embodiment of the present invention is applied.
  • the engine 1 is, for example, a marine 2-cycle large diesel engine.
  • the engine 1 includes a cylinder 2, a piston 3 that is reciprocally disposed in the cylinder 2, and a cylinder head 4 that covers one end of the cylinder 2.
  • a combustion chamber 5 is defined by the cylinder 2, the piston 3 and the cylinder head 4.
  • the engine 1 has, for example, a crosshead structure, and a piston rod 3a extends from the opposite side of the piston 3 to the combustion chamber 5, and the piston rod 3a penetrates the other end side of the cylinder 2.
  • the opposite side of the piston rod 3a to the piston 3 is connected to a crankshaft in the crank chamber via a crosshead and a connecting rod.
  • an exhaust port is provided in the cylinder head 4 and a scavenging port (not shown) is provided on the other end side of the cylinder 2.
  • the piston ring 10 is attached to the outer periphery of the piston 3. Specifically, a piston ring groove 6 is formed on the outer peripheral portion of the piston 3, and the piston ring 10 is fitted in the piston ring groove 6.
  • the piston ring 10 is disposed coaxially with the cylinder 2 and the piston 3, and the axis line CL of the piston ring 10 coincides with the axis line of the cylinder 2 and the piston 3.
  • the piston ring 10 protrudes outward from the outer peripheral surface of the piston 3 in the radial direction of the piston 3, and has an outer peripheral surface in sliding contact with the inner peripheral surface (cylinder inner peripheral surface) 2a of the cylinder 2. Therefore, the gap between the cylinder inner peripheral surface 2 a and the outer peripheral surface of the piston 3 is closed by the piston ring 10, and the pressure of the combustion chamber 5 can be held by the piston ring 10.
  • piston rings 60, 70, and 80 are attached to the piston 3 with an interval in the direction along the axis line CL (hereinafter also referred to as the axial direction). Yes.
  • the piston ring 10 is disposed closest to the combustion chamber 5 in the axial direction.
  • the total number of piston rings is not limited to four, and may be three, for example.
  • FIG. 2 is a perspective view schematically showing the piston ring 10.
  • the piston ring 10 includes a main body portion 10 a, and a first tongue portion 12 and a second tongue portion 13 that form the joint portion 11.
  • the main body 10a extends along the circumferential direction around the axis CL.
  • FIG. 3 is a plan view schematically showing a region A in FIG. 2
  • FIG. 4 is a perspective view schematically showing the region A in FIG.
  • the first tongue portion 12 extends from one end of the main body portion 10 a in the circumferential direction.
  • the first tongue 12 includes an inner peripheral piece 12a that forms the inner peripheral side of the piston ring 10, and a contact piece that protrudes radially outward from the combustion chamber 5 side in the axial direction of the inner peripheral piece 12a. 12b.
  • the inner peripheral piece 12a and the contact piece 12b have an L-shaped cross-sectional shape in a cross section orthogonal to the circumferential direction, and form a fitting groove 12c extending in the circumferential direction.
  • the fitting groove 12c is located on the outer side in the radial direction of the main body 10a, and is located on the crosshead side (crank chamber side) in the axial direction.
  • the second tongue portion 13 extends from the other end of the main body portion 10a in the circumferential direction.
  • the cross-sectional shape of the second tongue portion 13 is formed in a rectangular shape, and the second tongue portion 13 includes the radial outer surface of the inner peripheral piece 12a and the axial cross of the contact piece 12b. It has two side surfaces respectively facing the head side surface.
  • the outer peripheral surface of the piston ring 10 is formed by the side surface 12 d of the first tongue portion 12 and the side surface 13 d of the second tongue portion 13.
  • the side surface 12d of the first tongue portion 12 is the side surface of the contact piece 12b.
  • the side surface 12d of the first tongue portion 12 is located outside in the radial direction of the main body portion 10a and faces outward in the radial direction.
  • the side surface 12d extends along the circumferential direction, and is opposed to the cylinder inner circumferential surface 2a when the piston ring 10 is mounted on the piston 3.
  • the side surface 12d of the first tongue portion 12 is also referred to as an outer peripheral surface 12d.
  • the outer peripheral surface 12d of the first tongue 12 is a side surface of the contact piece 12b.
  • the side surface 13d of the second tongue portion 13 is located outside in the radial direction of the main body portion 10a and faces radially outward.
  • the side surface 13d extends along the circumferential direction, and is opposed to the cylinder inner circumferential surface 2a when the piston ring 10 is mounted on the piston 3.
  • the side surface 13d of the second tongue portion 13 is also referred to as an outer peripheral surface 13d.
  • the first tongue portion 12 and the second tongue portion 13 are disposed in the axial direction at the joint portion 11.
  • a non-overlapping region S1 that does not overlap with the first tongue 12 is present in the vicinity of the root of the first tongue 12.
  • a communication groove G1 is formed on the outer peripheral surface 12d of the first tongue 12 in the non-overlapping region S1, that is, on the outer peripheral surface of the contact piece 12b.
  • the communication groove G1 extends in the axial direction and opens on both sides of the contact piece 12b of the first tongue portion 12 in the axial direction. Therefore, the communication groove G1 communicates the combustion chamber 5 side and the crank chamber side in the axial direction. Further, the communication groove G1 opens outward in the radial direction.
  • the piston ring 10 is heated by the combustion gas and becomes high temperature.
  • the temperature on the inner peripheral side of the piston ring 10 becomes higher than the temperature on the outer peripheral side.
  • the amount of thermal expansion of the piston ring 10 is larger on the inner peripheral side than on the outer peripheral side, and the joint portion 11 of the piston ring 10 is thermally deformed so as to expand outward in the radial direction of the piston ring 10.
  • the contact surface pressure between the first tongue portion 12 and the second tongue portion 13 constituting the joint portion 11 and the cylinder inner peripheral surface 2a is increased, and the cylinder inner peripheral surface 2a is formed in the vicinity of the joint portion 11. Uneven wear occurs.
  • the curvature radii of the first tongue 12 and the second tongue 13 are changed to the inner circumference of the cylinder. It becomes larger than the curvature radius of the surface 2a, and the base side of the first tongue portion 12 and the second tongue portion 13 is easily separated from the cylinder inner peripheral surface 2a.
  • the combustion gas can escape through the communication groove G1. It is possible to suppress high-temperature combustion gas from blowing through at high pressure and high speed in the non-overlapping region S1. As a result, damage in the non-overlapping region S1 is suppressed, and the durability of the piston ring 10 is improved. Further, by providing the communication groove G1, the rigidity of the first tongue 12 is reduced, and the contact surface pressure of the piston ring 10 with respect to the cylinder inner peripheral surface 2a is made uniform. As a result, uneven wear of the piston ring 10 and the cylinder inner peripheral surface 2a is suppressed, and the durability of the piston ring 10 is improved.
  • the cross-sectional shape of the communication groove G1 in the cross section orthogonal to the axis CL is formed in a semicircular shape. According to this configuration, by making the cross-sectional shape of the communication groove G1 in the cross section orthogonal to the axis CL a semicircular shape, the change in the cross-sectional shape near the communication groove G1 becomes smooth. As a result, the stress concentration in the vicinity of the communication groove G1 is relaxed, and the durability of the piston ring 10 can be improved.
  • FIG. 5 is a perspective view schematically showing an enlarged part of the piston ring 20.
  • the piston ring 20 is formed on the outer peripheral surface 13d of the second tongue 13 in a non-overlapping region S2 near the root of the second tongue 13 where the first tongue 12 and the second tongue 13 do not overlap in the axial direction.
  • the second embodiment is different from the first embodiment in that the communication groove G2 is formed.
  • the communication groove G2 extends in the axial direction and opens on both sides of the second tongue 13 in the axial direction. Further, the communication groove G2 opens outward in the radial direction of the main body portion 10a.
  • the combustion gas can escape through the communication groove G2, and the non-overlapping region S2 In the region S2, the high-temperature combustion gas is suppressed from blowing through at high pressure and high speed.
  • damage in the non-overlapping region S2 is suppressed, and the durability of the piston ring 20 is improved.
  • the rigidity of the second tongue portion 13 is reduced, and the contact surface pressure of the piston ring 20 with respect to the cylinder inner peripheral surface 2a is made uniform. As a result, uneven wear of the piston ring 20 and the cylinder inner peripheral surface 2a is suppressed, and the durability of the piston ring 20 is improved.
  • the cross-sectional shape of the communication groove G2 in the cross section orthogonal to the axis line CL is formed in a semicircular shape. According to this configuration, by changing the cross-sectional shape of the communication groove G2 in the cross section orthogonal to the axis CL to a semicircular shape, the change in the cross-sectional shape near the communication groove G2 becomes smooth. As a result, stress concentration in the vicinity of the communication groove G2 is alleviated, and the durability of the piston ring 20 can be improved.
  • FIG. 6 is a perspective view schematically showing an enlarged part of the piston ring 30.
  • the piston ring 30 has an outer peripheral surface 12d of the first tongue 12 and an outer periphery of the second tongue 13 in the non-overlapping regions S1 and S2 where the first tongue 12 and the second tongue 13 do not overlap in the axial direction.
  • the first and second embodiments are different in that communication grooves G1 and G2 are formed on the surface 13d.
  • FIG. 7 is an enlarged perspective view schematically showing a part of the piston ring 40.
  • the cross-sectional area of the communication grooves G3 and G4 in the cross section orthogonal to the axis CL is the axis CL.
  • the communication grooves G3 and G4 extend in the axial direction, and open on both sides of the contact piece 12b of the first tongue portion 12 and the second tongue portion 13 in the axial direction.
  • the communication grooves G3 and G4 are opened outward in the radial direction of the main body 10a.
  • the cross-sectional area of the communication grooves G3 and G4 increases from one side to the other side in the direction along the axis CL, so that the combustion gas flows from one side to the other side.
  • the speed of the combustion gas flowing out from the other side of the communication grooves G3, G4 can be reduced.
  • the cross-sectional area of the communication grooves G3 and G4 increases from the combustion chamber 5 side to the crosshead side (crank chamber)
  • fuel flows from the combustion chamber 5 side to the crank chamber side.
  • the speed of the combustion gas flowing out from the crosshead side of G3 and G4 can be reduced. Therefore, as shown in FIG. 1, when another piston ring 60 is arranged next to the piston ring 10, for example, on the crank chamber side, the collision pressure of the combustion gas to the other piston ring 60 can be reduced.
  • the durability of the piston ring 60 is improved.
  • the present invention is not limited to the first to fourth embodiments described above, and includes forms obtained by modifying these embodiments and forms obtained by combining these embodiments.
  • the cross-sectional shape of the communication grooves G1, G2 is preferably a semicircular shape, but may be a V shape, a rectangular shape, or the like.
  • the piston ring which concerns on this invention is suitable for a marine 2-cycle large-sized diesel engine, of course, you may apply to another engine etc.

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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)
PCT/JP2014/071441 2014-02-25 2014-08-14 ピストンリング及び該ピストンリングを備えるエンジン WO2015129074A1 (ja)

Priority Applications (2)

Application Number Priority Date Filing Date Title
CN201480073889.4A CN105934612A (zh) 2014-02-25 2014-08-14 活塞环以及具有该活塞环的发动机
KR1020167014342A KR101823807B1 (ko) 2014-02-25 2014-08-14 피스톤 링 및 그 피스톤 링을 구비하는 엔진

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2014033803A JP6062382B2 (ja) 2014-02-25 2014-02-25 ピストンリング及び該ピストンリングを備えるエンジン
JP2014-033803 2014-02-25

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WO2015129074A1 true WO2015129074A1 (ja) 2015-09-03

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PCT/JP2014/071441 WO2015129074A1 (ja) 2014-02-25 2014-08-14 ピストンリング及び該ピストンリングを備えるエンジン

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JP (1) JP6062382B2 (zh)
KR (1) KR101823807B1 (zh)
CN (1) CN105934612A (zh)
WO (1) WO2015129074A1 (zh)

Cited By (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116696586A (zh) * 2022-03-02 2023-09-05 曼能解决方案（曼能解决方案德国股份公司）分公司 用于大型二冲程涡轮增压单流扫气十字头内燃机的活塞环

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
EP3889472B1 (en) * 2020-04-02 2024-06-19 Winterthur Gas & Diesel Ltd. Piston ring package
JP7307778B2 (ja) * 2021-09-30 2023-07-12 Ｔｐｒ株式会社 ピストンリングの組合せ、及び内燃機関

Citations (5)

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JPS5566543U (zh) * 1978-11-01 1980-05-08
JPS566957A (en) * 1979-06-01 1981-01-24 Cattaneo Leopoldo Piston ring
JPH0419951U (zh) * 1990-06-12 1992-02-19
US5779243A (en) * 1996-11-21 1998-07-14 Delaware Capital Formation, Inc. Piston ring set for reciprocating engines
JP2004522914A (ja) * 2001-03-08 2004-07-29 エムエーエヌ・ビー・アンド・ダブリュ・ディーゼル・エーエス 往復機関

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US1494140A (en) * 1921-07-12 1924-05-13 Frank E Small Piston packing
JPS55166947U (zh) * 1979-05-18 1980-12-01
JPH07332496A (ja) 1994-06-08 1995-12-22 Toyota Motor Corp 内燃機関のピストンリング
US5934680A (en) * 1995-05-31 1999-08-10 Ntn Corporation Split resin seal ring with chamfered end connection structures
JP2001241357A (ja) 2000-02-28 2001-09-07 Nippon Piston Ring Co Ltd ピストンリングの組合せおよびその組合せを用いたピストン
CN2523973Y (zh) * 2001-12-26 2002-12-04 杨武成 直角面单向密封达口活塞环
CN201065795Y (zh) * 2007-08-08 2008-05-28 宋长英 一种活塞环
JP5781332B2 (ja) * 2011-02-28 2015-09-24 三菱重工業株式会社 ピストンリング

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5566543U (zh) * 1978-11-01 1980-05-08
JPS566957A (en) * 1979-06-01 1981-01-24 Cattaneo Leopoldo Piston ring
JPH0419951U (zh) * 1990-06-12 1992-02-19
US5779243A (en) * 1996-11-21 1998-07-14 Delaware Capital Formation, Inc. Piston ring set for reciprocating engines
JP2004522914A (ja) * 2001-03-08 2004-07-29 エムエーエヌ・ビー・アンド・ダブリュ・ディーゼル・エーエス 往復機関

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN116696586A (zh) * 2022-03-02 2023-09-05 曼能解决方案（曼能解决方案德国股份公司）分公司 用于大型二冲程涡轮增压单流扫气十字头内燃机的活塞环
CN116696586B (zh) * 2022-03-02 2024-06-07 曼能解决方案（曼能解决方案德国股份公司）分公司 用于大型二冲程涡轮增压单流扫气十字头内燃机的活塞环

Also Published As

Publication number Publication date
KR101823807B1 (ko) 2018-01-30
KR20160079066A (ko) 2016-07-05
JP2015158247A (ja) 2015-09-03
CN105934612A (zh) 2016-09-07
JP6062382B2 (ja) 2017-01-18

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