WO2003069147A1 - Culasse de cylindre - Google Patents
Culasse de cylindre Download PDFInfo
- Publication number
- WO2003069147A1 WO2003069147A1 PCT/JP2002/001198 JP0201198W WO03069147A1 WO 2003069147 A1 WO2003069147 A1 WO 2003069147A1 JP 0201198 W JP0201198 W JP 0201198W WO 03069147 A1 WO03069147 A1 WO 03069147A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- seat ring
- cylinder head
- intake
- eccentric
- center
- Prior art date
Links
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
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4214—Shape or arrangement of intake or exhaust channels in cylinder heads specially adapted for four or more valves per cylinder
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
- F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
- F01L3/00—Lift-valve, i.e. cut-off apparatus with closure members having at least a component of their opening and closing motion perpendicular to the closing faces; Parts or accessories thereof
- F01L3/06—Valve members or valve-seats with means for guiding or deflecting the medium controlled thereby, e.g. producing a rotary motion of the drawn-in cylinder charge
-
- Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
- Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
- Y02T—CLIMATE CHANGE MITIGATION TECHNOLOGIES RELATED TO TRANSPORTATION
- Y02T10/00—Road transport of goods or passengers
- Y02T10/10—Internal combustion engine [ICE] based vehicles
- Y02T10/12—Improving ICE efficiencies
Definitions
- the present invention relates to a cylinder head capable of improving the combustibility of a lean burn gas engine and maintaining high engine thermal efficiency while maintaining low NOx.
- a seat ring is attached to an opening of an intake port communicating with a combustion chamber, and a seat surface is provided to abut an intake valve that opens and closes this opening.
- Fig. 11 shows an example of the shape of a conventional seat ring.
- This seat ring (hereinafter referred to as a standard seat ring) is annular, and its inner diameter ⁇ A and outer diameter F form concentric circles. That is, in a c- gas engine having the same center a as the inner diameter ⁇ ⁇ and the outer diameter F, the combustion of the mixture of fuel gas and air is performed by flame propagation. Therefore, active utilization of air flow contributes to improvement of thermal efficiency by shortening combustion time.
- the cylinder head of this pilot oil-ignited gas engine has a high flow coefficient because of the common use with a diesel engine, but has a zero swelling ratio, thus improving the flammability using the flow of air. Can't expect.
- the present invention has been made in view of the above circumstances, and provides a cylinder head capable of maintaining a flow coefficient and enhancing a swirl flow, which are contradictory elements, to improve thermal efficiency. With the goal. Summary of the Invention
- the present invention provides a silling head in which a seat ring to which an intake valve abuts is attached to each of a plurality of intake ports communicating with a combustion chamber of an internal combustion engine.
- An eccentric seat ring with the center of the inner diameter eccentric was attached.
- the intake port was mixed with an intake port with a standard seat ring with the center of the outer diameter and the center of the inner diameter attached. It is a thing.
- the intake port with the eccentric seat ring and the intake port with the standard seat ring are mixed, and as a result, the flow coefficient is increased by the intake port with the standard seat.
- the swirl flow is enhanced by the intake port equipped with the eccentric seat ring while being secured. As a result, it is possible to ensure both the flow coefficient, which is the contradictory factor, and strengthen the swirl flow, which is higher than when only the standard seating is installed or when only the eccentric seating is installed. Thermal efficiency is obtained.
- two intake ports are provided along the direction from the intake manifold side to the opposite side across the cylinder head, and one of the intake ports is provided with a standard seal. Attach the tring and attach the eccentric seat ring to the other intake port.
- the camshaft is located on the opposite side of the cylinder head from the intake manifold side, and the intake port is connected between the intake manifold side of the cylinder head and the power shaft side. It is also possible to install two standard seat rings on one intake port and an eccentric seat ring on the other intake port.
- a standard seat ring is attached to one of the intake boats, and the other is provided with a standard seat ring.
- An eccentric seating is attached to the intake port.
- the eccentric seat ring is attached to an intake port located at a relatively distant position when viewed from the intake manifold side.
- the cylinder head is provided with two exhaust ports that are parallel to the two intake ports, and the narrow portion of the eccentric seat ring edge is directed from the manifold side to the cylinder head.
- To the exhaust port side at an angle of about 45 ° to.
- an eccentric seat ring is attached to the intake port located relatively far from the intake manifold side, and the narrow part of the eccentric seat ring is removed from the manifold side. Approximately 45 in the direction toward the cylinder head. By directing it toward the exhaust port at an angle of ⁇ , the wall surface of the cylinder liner can be used effectively, and swirl flow can be generated effectively in the combustion chamber. In addition, since the direction of air intake is along the wall of the cylinder liner and has little interference with the air intake from the air intake port equipped with the standard seating, the air flow is strengthened and the air flow is enhanced. The flow coefficient can be secured.
- FIG. 1 is a sectional view of an eccentric seating used for a cylinder head according to the present invention.
- FIG. 2 is a plan view of the eccentric seat ring shown in FIG.
- FIG. 3A is a plan view showing a variation (No. 1) of a combination of seat rings attached to a cylinder head.
- FIG. 3B is a plan view showing a variation (No. 2) of a combination of a seat ring attached to a cylinder head.
- FIG. 3C is a plan view showing a variation (No. 3) of a combination of the seat rings attached to the cylinder head.
- FIG. 4A is a plan view showing a variation (No. 4) of a combination of seat rings attached to a cylinder head.
- FIG. 4B is a plan view showing a variation (No. 5) of a combination of a seat ring attached to a cylinder head.
- FIG. 4C is a plan view showing the variation (No. 6) of the combination of the seat rings attached to the cylinder head.
- FIG. 5A is a plan view showing a variation (No. 7) of a combination of seat rings attached to a cylinder head.
- FIG. 5B is a plan view showing a variation (No. 8) of the combination of the seat rings attached to the cylinder head.
- FIG. 5C is a plan view showing a variation (No. 9) of a combination of seat rings attached to the cylinder head.
- FIG. 6A is a plan view showing a variation (No. 10) of a combination of seat rings attached to a cylinder head.
- FIG. 6B is a plan view showing a variation (No. 11) of the combination of the seat rings attached to the cylinder head.
- FIG. 6C is a plan view showing a variation (No. 12) of the combination of the seat ring attached to the cylinder head.
- Figure 7A shows a Paris view of a combination of seat rings mounted on a cylinder head. It is a top view which shows an essence (No. 13).
- FIG. 7B is a plan view showing a variation (No. 14) of the combination of the seat rings attached to the cylinder head.
- FIG. 7C is a plan view showing a combination (No. 15) of a combination of seat rings attached to a cylinder head.
- FIG. 8 is a graph showing the flow coefficient and the number of dimensionless swirls in the variation of the combination of the seating shown in FIGS. 3A to 7C.
- FIG. 9 is a plan view of a cylinder head having a seating configuration corresponding to the combination No. 11 shown in FIG. 6B.
- FIG. 10 is a graph comparing the thermal efficiency of the engine having the cylinder head shown in FIG. 9 with the engine having only the standard seat ring.
- FIG. 11 is a cross-sectional view of a standard seat ring used for a conventional cylinder head. Preferred embodiment
- the present invention appropriately selects a mounting portion and an eccentric direction of a seat ring for an intake port attached to a cylinder head of a gas engine, enhances a swirl flow without reducing a flow coefficient, This is to promote air flow and improve flammability.
- INDUSTRIAL APPLICABILITY The present invention is applicable to an engine in which a mixture is burned by flame propagation, that is, a pilot oil-ignition gas engine, a spark ignition gas engine, a spark ignition gasoline engine, and the like.
- the engine employing the technology of the present invention is used, for example, in stationary power generation facilities for industrial or consumer use.
- FIG. 1 is a cross-sectional view of a seat ring (hereinafter, referred to as an eccentric seat ring) used in a shilling head according to the present invention
- FIG. 2 is a plan view of the eccentric seat ring shown in FIG.
- the eccentric seat ring 1 shown in FIG. 1 is attached to the opening of the intake port opened to the cylinder head.
- the eccentric seat ring 1 has a hole 3 that opens to the intake port side.
- An inlet portion 5 having a seat surface 7 provided on the combustion chamber side and having a seat surface 7 with which an intake valve comes into contact, a fitting portion 11 to be attached to an opening of a cylinder head, and the like. .
- the center of the outer diameter does not coincide with the center of the inner diameter of the hole 3. That is, in the eccentric seat ring 1, the center of the inner diameter of the hole 3 is eccentric with respect to the center of the outer diameter.
- a peripheral surface of an inner diameter ⁇ B having a center b eccentric by E from the outer diameter center a forms an inner peripheral surface of the hole 3.
- the direction from the center a of the outer diameter to the center b of the inner diameter is referred to as the eccentric direction of the eccentric seating 1.
- a peripheral surface having an inner diameter ⁇ A having the same center a as the outer diameter is formed, and then the peripheral surface is cut to form a peripheral surface having an inner diameter ⁇ .
- the portion of the inner peripheral surface of the hole 3 opposite to the eccentric direction of the eccentric seat ring 1 has a convex peripheral surface when the peripheral surface of the inner diameter ⁇ A is formed.
- the upper and lower widths of the flat peripheral surface 3b are the largest on the eccentric direction side of the eccentric seat ring 1 (the left side in FIG. 1).
- the intake port opening has a standard seat ring as shown in Fig. 11 in which the center a of the outer diameter and the center of the inner diameter ⁇ A of the hole 3 match. Attached. In this standard seat ring, the hole 3 and the outer diameter are concentric.
- the intake port to which the eccentric seat ring 1 is attached and the intake port to which the standard seat ring is attached are mixed.
- 3A to 7C are plan views schematically showing the cylinder head.
- This cylinder head has two openings A, B and two openings (:, D) for one cylinder.
- the left side is the camshaft side
- the right side is the manifold.
- ⁇ side Bottom the intake manifold and the exhaust manifold are on the same side).
- one ends of two intake ports 13 and 14 indicated by broken lines in FIG. 3A are connected to the combustion chamber through openings A and B. These openings A and B are respectively opened and closed by intake valves (not shown). Further, although not shown, the other ends of the intake ports 13 and 14 are connected to each other so as to have an upstream and downstream relationship with respect to the flow of the intake air.
- openings A and B are arranged such that a line passing through the center of each of the openings A and B extends from the manifold side to the opposite side (cam shaft side in the example in the figure) with the cylinder head interposed therebetween. I have.
- the openings C and D of the exhaust ports (not shown) connected to the combustion chamber are arranged in parallel with the openings B and B of the intake ports 13 and 14, respectively. These openings C and D are opened and closed by exhaust valves (not shown), respectively.
- Figures 3A to 7C show a total of 15 leaves. The positions of the standard and eccentric seat rings attached to each of the openings A to D in the steady flow test and the eccentric seat ring The combination with the eccentric direction is shown. 3A to 7C, the center of the outer diameter of the eccentric seat ring coincides with the center of the opening to which the eccentric seat ring is attached. 3A to 7C, the arrow d indicates the eccentric direction of the eccentric seat ring.
- the flow coefficient and swirl flow were targeted at a flow coefficient of 0.51 and a non-dimensional number of spirals of 0.14, which are comparable to those of conventional gas engines.
- the conventional gas engine has a low output per unit cylinder volume, and when expressed using BMEP, it has a small output of less than 1.23 MPa and a maximum of less than 1.47 MPa. No combustion air was required.
- the contradictory factors of flow coefficient and swirl flow should be set to appropriate values without using special technology. It was possible.
- the output per cylinder volume is 1.47MPa or more in BMEP, preferably 1 .72MPa or more, more preferably 1.
- the intake port must be designed with an emphasis on the flow coefficient because a larger amount of air is required than before. Not get.
- the swirl flow must be set to an appropriate value to promote the flame propagation of the air-fuel mixture starting from the ignition source in the cylinder of the gas engine and to ensure the combustion of the air-fuel mixture.
- the swirl flow cannot be made as strong as the conventional gas engine.
- the flow coefficient 0.51 and the dimensionless dimension comparable to those of a conventional gas engine are used.
- the swirl number was set at 0.134.
- the combination of the standard seat ring and the eccentric seat ring maintains the same flow coefficient and the number of dimensionless wheels as the conventional gas engine, thereby reducing the number of cylinders per cylinder.
- the aim is to improve the economic efficiency by reducing the initial cost and the running cost by improving the engine power generation efficiency.
- FIG. 8 shows the flow coefficient and the number of dimensionless swirls at the maximum valve lift in the combinations of the various seal rings shown in FIGS. 3A to 7C.
- the dimensionless swirl number on the vertical axis in Fig. 8 indicates the direction of the swirl flow, and as shown in Fig. 3A, the counterclockwise direction is 10 and the clockwise direction is 1 when viewed from the explosion surface of the shilling head. It is.
- one of the openings A and B has a standard seat ring and the other has a standard seat ring.
- An eccentric seat ring was attached to each (combinations No. 8 to No. 15), and the relationship between the direction of the eccentric seat ring and the air fluidity was evaluated.
- the opening B is relatively far away from the intake manifold side, it is considered that the effect of using the wall surface of the cylinder liner to generate a swirl flow was obtained. Also in this case, by attaching a standard seed ring to the opening A, a flow coefficient of about 0.54 to 0.55 is secured.
- the standard sheet is provided.
- the flow coefficient is ensured by the intake port to which the ring is attached, and the swirl flow is reinforced by the intake port to which the eccentric seat ring 1 is attached.
- Fig. 9 is a plan view showing the cylinder head of an engine with a seat ring configuration equivalent to combination No. 11, and Fig. 10 compares the thermal efficiency of the engine shown in Fig. 9 with the engine fitted with a standard seat ring. It is the graph which did.
- the engine according to this embodiment is a 6-cylinder engine with a cylinder diameter of 220 mm.
- the cylinder head is equipped with a seat ring having a seating configuration of combination No. 11 (Fig. 6B). That is, an eccentric seat ring is provided at an intake port located relatively far from the intake manifold side, and the narrow portion of the eccentric seat ring has a cam, as shown by an arrow d in the figure. It is arranged toward the exhaust port side at an angle of about 45 ° from the shaft side.
- the thermal efficiency may be increased by 0.2 to 0.5 points as compared with the case where the standard seating is installed. Do you get it.
- the eccentric seat ring is attached to the intake port located relatively far from the intake manifold side, and the narrow portion of the edge of the eccentric seat ring is connected to the cam.
- the wall surface of the cylinder liner can be used effectively, and swirl flow can be generated effectively in the combustion chamber.
- the swirl flow is enhanced while the flow coefficient is reduced. It can be secured.
- an eccentric seat ring 1 having an asymmetrical shape on the left and right is provided with a convex peripheral surface having an inner diameter ⁇ A having the same center as the outer diameter center a.
- the eccentric peripheral surface of the inner diameter ⁇ ⁇ is formed by cutting, but the present invention is not limited to this.
- an eccentric seal ring having different thicknesses but substantially similar left and right shapes is formed by making the inner periphery a convex peripheral surface over the entire periphery, or making the inner periphery a flat peripheral surface over the entire periphery. Is also good.
- the eccentric seat ring 1 has an inner diameter ⁇ B larger than the inner diameter ⁇ A of the standard seat ring.
- the inside diameter is not always larger than the inside diameter of the standard seating.
- the inner diameter of the eccentric shuttle ring 1 may be smaller than the inner diameter of the standard seat ring.
- the eccentricity It is desirable that the inside diameter of one trolling be larger than the inside diameter of a standard seat ring. In the embodiment described above, as shown by the broken line in FIG.
- two intake ports 13 and 14 are respectively opened to the combustion chamber, and the other end of each intake port 13 and 14 is Although an example is shown in which the intake ports are connected to each other so as to have an upstream and downstream relationship with respect to the intake flow, a configuration in which each intake port is independently connected to the intake manifold may be employed.
- the left side is the camshaft side
- the right side is the manifold side (both the intake manifold and the exhaust manifold are on the same side).
- the intake manifold is provided on the shaft side so that it is located on the opposite side, the intake manifold may be configured to face the exhaust manifold via a cylinder. Good.
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
Description
Claims
Priority Applications (11)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000245820A JP3676967B2 (ja) | 2000-08-14 | 2000-08-14 | シリンダヘッド |
KR1020037013314A KR100827831B1 (ko) | 2002-02-13 | 2002-02-13 | 실린더 헤드 |
PCT/JP2002/001198 WO2003069147A1 (fr) | 2000-08-14 | 2002-02-13 | Culasse de cylindre |
CNB028081943A CN100458132C (zh) | 2000-08-14 | 2002-02-13 | 气缸头 |
ES02701542T ES2411006T3 (es) | 2002-02-13 | 2002-02-13 | Culata de cilindro |
US10/474,609 US7066131B2 (en) | 2000-08-14 | 2002-02-13 | Cylinder head |
DK02701542.9T DK1475529T3 (da) | 2000-08-14 | 2002-02-13 | Cylindertopstykke |
PT27015429T PT1475529E (pt) | 2000-08-14 | 2002-02-13 | Cabeça de cilindros |
EP02701542A EP1475529B1 (en) | 2000-08-14 | 2002-02-13 | Cylinder head |
NO20034535A NO337062B1 (no) | 2000-08-14 | 2003-10-09 | Sylinderhode |
CY20131100445T CY1114018T1 (el) | 2000-08-14 | 2013-06-04 | Κεφαλη κυλινδρου |
Applications Claiming Priority (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP2000245820A JP3676967B2 (ja) | 2000-08-14 | 2000-08-14 | シリンダヘッド |
PCT/JP2002/001198 WO2003069147A1 (fr) | 2000-08-14 | 2002-02-13 | Culasse de cylindre |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2003069147A1 true WO2003069147A1 (fr) | 2003-08-21 |
Family
ID=29422258
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2002/001198 WO2003069147A1 (fr) | 2000-08-14 | 2002-02-13 | Culasse de cylindre |
Country Status (9)
Country | Link |
---|---|
US (1) | US7066131B2 (ja) |
EP (1) | EP1475529B1 (ja) |
JP (1) | JP3676967B2 (ja) |
CN (1) | CN100458132C (ja) |
CY (1) | CY1114018T1 (ja) |
DK (1) | DK1475529T3 (ja) |
NO (1) | NO337062B1 (ja) |
PT (1) | PT1475529E (ja) |
WO (1) | WO2003069147A1 (ja) |
Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP7325878B1 (ja) * | 2023-02-28 | 2023-08-15 | ライズピットカンパニー株式会社 | ガスエンジン |
Families Citing this family (21)
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FR2911367B1 (fr) * | 2007-01-11 | 2011-04-15 | Peugeot Citroen Automobiles Sa | Siege de soupape usine en plusieurs chanfreins |
FR2911366B1 (fr) * | 2007-01-11 | 2009-04-17 | Peugeot Citroen Automobiles Sa | Siege de soupape usine en deux chanfreins desaxes |
FR2916798A3 (fr) * | 2007-06-01 | 2008-12-05 | Renault Sas | Siege de soupape anti-reflux |
JP4730355B2 (ja) * | 2007-08-29 | 2011-07-20 | トヨタ自動車株式会社 | 内燃機関のポート及びポート製造方法 |
US20100236533A1 (en) * | 2009-03-23 | 2010-09-23 | Riccardo Meldolesi | Valve Seat Insert for a Split-Cycle Engine |
EP2698508A1 (en) * | 2012-08-17 | 2014-02-19 | MWM GmbH | Cylinder head with countersink |
EP2940268B1 (en) | 2012-12-26 | 2020-02-05 | Doosan Infracore Co., Ltd. | Engine intake port structure |
CN103696868B (zh) * | 2013-12-10 | 2016-05-25 | 天津大学 | 具有高涡流与滚流比的内燃机缸盖 |
KR101916982B1 (ko) * | 2014-07-15 | 2018-11-08 | 현대중공업 주식회사 | 흡기 유동 패턴의 설정이 용이한 밸브 시트, 그것을 구비하는 실린더 헤드 및 시험용 실린더 헤드 장치 |
DE202014007837U1 (de) * | 2014-11-07 | 2016-02-11 | GM Global Technology Operations LLC (n. d. Ges. d. Staates Delaware) | Einlasskanal in einen Brennraum einer Brennkraftmaschine |
JP6600947B2 (ja) * | 2015-01-29 | 2019-11-06 | 三菱自動車工業株式会社 | エンジンの吸気ポート構造 |
JP6561480B2 (ja) * | 2015-01-29 | 2019-08-21 | 三菱自動車工業株式会社 | エンジンの吸気ポート構造 |
JP6455184B2 (ja) * | 2015-01-29 | 2019-01-23 | 三菱自動車工業株式会社 | エンジンの吸気ポート構造 |
US20160333751A1 (en) * | 2015-05-07 | 2016-11-17 | Frank J. Ardezzone | Engine Insert and Process for Installing |
CN105240138A (zh) * | 2015-11-02 | 2016-01-13 | 重庆金花玻璃钢有限公司 | 能改气门部冷却和热量损失的发动机缸盖 |
CN105240145A (zh) * | 2015-11-02 | 2016-01-13 | 重庆金花玻璃钢有限公司 | 耐磨型发动机缸盖 |
US10934899B2 (en) * | 2018-11-13 | 2021-03-02 | Caterpillar Inc. | Valve seat insert for engine having double-crowned seating surface profiled for limiting valve recession |
US11060425B2 (en) * | 2019-03-13 | 2021-07-13 | Caterpillar Inc. | Valve seat insert for engine head having venturi flow crowns and seating surface profiled for limiting valve recession |
JP7331784B2 (ja) * | 2020-06-01 | 2023-08-23 | Jfeエンジニアリング株式会社 | ディーゼルエンジン |
US11739681B2 (en) * | 2021-09-07 | 2023-08-29 | Southwest Research Institute | Far square tumble flow engine |
US11655777B2 (en) | 2021-09-07 | 2023-05-23 | Southwest Research Institute | Parallel intake valve tumble flow engine |
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JP2002004821A (ja) * | 2000-06-20 | 2002-01-09 | Honda Motor Co Ltd | 内燃機関の弁座 |
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2000
- 2000-08-14 JP JP2000245820A patent/JP3676967B2/ja not_active Expired - Lifetime
-
2002
- 2002-02-13 CN CNB028081943A patent/CN100458132C/zh not_active Expired - Lifetime
- 2002-02-13 DK DK02701542.9T patent/DK1475529T3/da active
- 2002-02-13 EP EP02701542A patent/EP1475529B1/en not_active Expired - Lifetime
- 2002-02-13 WO PCT/JP2002/001198 patent/WO2003069147A1/ja active Application Filing
- 2002-02-13 PT PT27015429T patent/PT1475529E/pt unknown
- 2002-02-13 US US10/474,609 patent/US7066131B2/en not_active Expired - Lifetime
-
2003
- 2003-10-09 NO NO20034535A patent/NO337062B1/no not_active IP Right Cessation
-
2013
- 2013-06-04 CY CY20131100445T patent/CY1114018T1/el unknown
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JP2000027612A (ja) * | 1998-07-10 | 2000-01-25 | Niigata Eng Co Ltd | 吸気弁のシートリング及びガスエンジン |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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JP7325878B1 (ja) * | 2023-02-28 | 2023-08-15 | ライズピットカンパニー株式会社 | ガスエンジン |
Also Published As
Publication number | Publication date |
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EP1475529A4 (en) | 2011-06-22 |
EP1475529B1 (en) | 2013-03-06 |
CN1522338A (zh) | 2004-08-18 |
US7066131B2 (en) | 2006-06-27 |
US20040084005A1 (en) | 2004-05-06 |
JP2002054445A (ja) | 2002-02-20 |
DK1475529T3 (da) | 2013-06-10 |
EP1475529A1 (en) | 2004-11-10 |
NO20034535D0 (no) | 2003-10-09 |
CY1114018T1 (el) | 2016-07-27 |
PT1475529E (pt) | 2013-06-12 |
NO337062B1 (no) | 2016-01-11 |
JP3676967B2 (ja) | 2005-07-27 |
NO20034535L (no) | 2003-10-09 |
CN100458132C (zh) | 2009-02-04 |
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