WO2011099156A1 - 内燃機関のピストン - Google Patents
内燃機関のピストン Download PDFInfo
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- WO2011099156A1 WO2011099156A1 PCT/JP2010/052159 JP2010052159W WO2011099156A1 WO 2011099156 A1 WO2011099156 A1 WO 2011099156A1 JP 2010052159 W JP2010052159 W JP 2010052159W WO 2011099156 A1 WO2011099156 A1 WO 2011099156A1
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- WIPO (PCT)
- Prior art keywords
- piston
- region
- crown surface
- tumble flow
- internal combustion
- Prior art date
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Classifications
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- 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
- F02F3/02—Pistons having means for accommodating or controlling heat expansion
- F02F3/04—Pistons having means for accommodating or controlling heat expansion having expansion-controlling inserts
- F02F3/08—Pistons having means for accommodating or controlling heat expansion having expansion-controlling inserts the inserts being ring-shaped
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B23/104—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder the injector being placed on a side position of the cylinder
-
- 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
- F02F3/10—Pistons having surface coverings
- F02F3/12—Pistons having surface coverings on piston heads
- F02F3/14—Pistons having surface coverings on piston heads within combustion chambers
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02B—INTERNAL-COMBUSTION PISTON ENGINES; COMBUSTION ENGINES IN GENERAL
- F02B23/00—Other engines characterised by special shape or construction of combustion chambers to improve operation
- F02B23/08—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition
- F02B23/10—Other engines characterised by special shape or construction of combustion chambers to improve operation with positive ignition with separate admission of air and fuel into cylinder
- F02B2023/106—Tumble flow, i.e. the axis of rotation of the main charge flow motion is horizontal
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- 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
- This invention relates to a piston of an internal combustion engine.
- a piston of an internal combustion engine in which a non-heat-insulating region is provided in a region of a piston crown surface that is lateral to the intake flow and a heat-insulating region is provided in other regions.
- a heat-insulating region is provided in other regions.
- a strong intake flow strikes the piston crown during the intake stroke.
- the heat conductivity is high, and therefore the intake gas is heated by the piston crown surface.
- a heat insulating region is provided in a region where a strong intake flow is applied, and the cooling loss is small, but the temperature of the heat insulating region is high. For this reason, the amount of heating of the intake gas by the piston crown surface increases. If the amount of heating of the intake gas increases, the temperature of the intake gas at the compression end increases, which may cause knocking.
- the present invention has been made in order to solve the above-described problems, and in an internal combustion engine in which a tumble flow is formed in a cylinder, the internal combustion engine capable of achieving both suppression of knocking and reduction of cooling loss.
- the object is to provide an engine piston.
- a first invention is a piston of an internal combustion engine in which a tumble flow is formed in a cylinder, A region on the piston crown where the tumble flow abuts during the intake stroke, and a non-insulated region without a heat insulating layer; It is an at least partial region on the piston crown surface other than the non-insulating region, and a heat insulating region having a heat insulating layer.
- the second invention is a piston of an internal combustion engine, A non-heat-insulating region having no heat insulating layer, which includes a central portion of the piston crown surface and is provided in a strip shape over the intake side and the exhaust side of the piston crown surface; And a heat insulating region having a heat insulating layer provided on the crown surface of the piston corresponding to the side of the non-insulating region.
- a third invention is a piston of an internal combustion engine in which a tumble flow is formed in a cylinder in order to achieve the above object,
- a non-insulating region having no heat insulating layer including at least a tumble flow contact region that is provided on a piston crown surface and in contact with the tumble flow during an intake stroke; And a heat insulating member provided inside the piston around the tumble flow contact area.
- a piston for an internal combustion engine for achieving the above object.
- the region of the piston crown surface other than the region where the tumble flow abuts can be set as the heat insulating region.
- the region of the piston crown surface with which the tumble flow abuts can be set as a non-adiabatic region. In the non-adiabatic region, the temperature of the piston crown surface is reduced as compared with the adiabatic region. In the region where the tumble flow abuts, the thermal conductivity is high.
- the temperature is reduced by using the non-adiabatic region, the amount of intake gas heated by the piston crown surface can be reduced. As a result, the temperature of the intake gas at the compression end is reduced, and knocking can be suppressed. For this reason, according to the present invention, in an internal combustion engine in which a tumble flow is formed in a cylinder, it is possible to achieve both suppression of knocking and reduction of cooling loss.
- the temperature of the region where the tumble flow abuts can be kept low.
- the region of the piston crown surface where the tumble flow abuts has high thermal conductivity. Therefore, heat is transferred from the piston to the intake gas, and the temperature of the region is lowered. At this time, heat moves from the other region of the piston that is at a high temperature to the region where the temperature has decreased, and tries to maintain equilibrium.
- this heat transfer can be blocked by the heat insulating member provided inside the piston. Therefore, the temperature of the region where the tumble flow abuts can be kept low, and the amount of intake gas heating by the piston crown surface can be reduced. For this reason, according to the present invention, the temperature of the intake gas at the compression end is reduced, and knocking can be suppressed.
- FIG. 1 is a diagram for explaining a system configuration of an internal combustion engine 10 according to Embodiment 1 of the present invention.
- the system of this embodiment includes an internal combustion engine 10.
- the internal combustion engine 10 is a four-cycle engine.
- FIG. 1 shows a longitudinal section of the internal combustion engine 10.
- the internal combustion engine 10 includes a cylinder block 12.
- a cylinder 14 is formed in the cylinder block 12.
- the number of cylinders of the internal combustion engine 10 is not particularly limited.
- a piston 16 is slidably disposed inside the cylinder 14. The piston 16 is connected to the crankshaft via a piston pin 18 and a connecting rod 20.
- the cylinder head 22 is assembled to the upper part of the cylinder block 12.
- a combustion chamber 24 of the internal combustion engine 10 is formed by a space surrounded by the inner surface of the cylinder 14 formed in the cylinder block 12, the crown surface of the piston 16, and the concave portion of the lower surface of the cylinder head 22.
- An ignition plug 26 is attached to the cylinder head 22 so as to protrude from the top of the combustion chamber 24 into the combustion chamber 24.
- the cylinder head 22 has an intake port 28 and an exhaust port 30 communicating with the combustion chamber 24.
- An injector (not shown) for injecting fuel into the intake port 28 is arranged upstream of the intake port 28 toward the combustion chamber 24.
- the system of the present embodiment includes an ECU (Electronic Control Unit) (not shown).
- the above-described spark plug 26 and injector are connected to the ECU.
- the ECU injects fuel into the injector during the intake stroke, and spark-ignites the spark plug 26 during the compression stroke.
- the downstream portion of the intake port 28 is branched into two.
- An intake valve 32 for opening and closing the intake port 28 relative to the combustion chamber 24 is provided at the downstream end of the branched intake port 28.
- the upstream portion of the exhaust port 30 is branched into two.
- an exhaust valve 34 for opening and closing the exhaust port 30 with respect to the combustion chamber 24 is provided.
- the number of intake ports and exhaust ports and the number of intake valves and exhaust valves are not particularly limited.
- a spherical recess is formed in the central portion 36 of the crown surface 35 facing the combustion chamber of the piston 16.
- an oblique squish that is inclined upward from the outer edge toward the central portion 36 toward the central portion 36 is formed on the outer edge portion 38 of the crown surface 35.
- An oblique squish facing the outer edge 38 is also formed on the outer edge 40 of the recess on the lower surface of the cylinder head 22 forming the combustion chamber 24. That is, a squish area is formed between the outer edge portions 38 and 40.
- FIG. 2 is a view for explaining the structure of the crown surface 35 of the piston 16 according to the first embodiment of the present invention.
- FIG. 2 is a top view of the crown surface 35 of the piston 16 as viewed from the direction of arrow B in FIG.
- valve recesses 48 IN corresponding to the umbrella portions of the two intake valves 32 are formed on the crown surface 35 of the piston 16.
- valve recesses 48 EX corresponding to the umbrella portions of the two exhaust valves 34 are formed on the crown surface 35.
- the crown surface 35 is formed with four outer edge portions 38 that form the squish area described above with the valve recesses 48 IN and 48 EX interposed therebetween.
- FIG. 1 shows a typical flow of the intake air flow formed in the cylinder 14 in the intake stroke of the system of the present embodiment.
- the solid line arrow a1 indicates the flow of intake gas that is sucked from the intake port 28 and led to the upper surface portion 42 of the combustion chamber 24 along the back surface of the intake valve 32 facing the intake port 28 in the intake stroke. ing.
- a solid arrow a2 indicates the flow of the intake gas guided from the upper surface portion 42 of the combustion chamber 24 to the exhaust-side side wall 44 of the cylinder 14 along the umbrella surface of the exhaust valve 34 facing the combustion chamber 24 in the intake stroke.
- a solid arrow a3 indicates the flow of the intake gas that is brought into contact with the crown surface 35 from the exhaust-side side wall 44 of the cylinder 14 and is guided to the intake-side side wall 46 of the cylinder 14 in the intake stroke.
- tumble flows indicated by solid arrows a1 to a3 are formed.
- the direction of the solid arrow a3 is perpendicular to the axis of the piston pin 18.
- the broken line arrow a3 shown in FIG. 2 indicates the flow of the intake gas that contacts the crown surface 35 in the intake stroke, similarly to the solid line arrow a3 in FIG.
- a region 50 on the crown surface 35 shown in FIG. 2 represents a region where the intake gas as a tumble flow flows in contact with the crown surface 35.
- the region 50 is referred to as a tumble flow contact region.
- the tumble flow contact region 50 is experimentally determined for each internal combustion engine. For example, an area where the tumble flow where the thermal conductivity of the crown surface 35 is equal to or greater than a threshold value is determined by an experiment or the like as the tumble flow contact area 50 where a strong air current strikes.
- the portion of the crown surface 35 other than the tumble flow contact region 50 is a region where a weak air flow having a thermal conductivity equal to or less than a threshold is applied, and is not a region where the tumble flow contacts.
- a tumble flow is formed in the intake stroke.
- the intake flow which is a tumble flow, flows from the exhaust side of the cylinder 14 toward the crown surface 35 of the piston 16 and passes toward the intake side of the cylinder 14 while contacting the crown surface 35. Therefore, a strong air current hits the tumble flow contact area 50 of the crown surface 35.
- At least a part on the crown surface 35 other than the tumble flow contact region 50 is defined as a heat insulating region in which a heat insulating layer is formed.
- the region 52 other than the tumble flow contact region 50 is a heat insulating region in which a heat insulating layer is formed.
- a region 52 heat insulating region
- a member having a heat insulating effect such as ceramic is used.
- the tumble flow contact region 50 where a strong air current strikes is set as a non-insulated region having no heat insulating layer.
- the tumble flow contact region 50 is experimentally determined for each internal combustion engine, and here, a representative example is shown.
- the long side of the tumble flow contact region 50 is determined so as to pass through the central portion 36 of the crown surface 35 from the position in contact with the exhaust side wall 44 to the position in contact with the intake side wall 46.
- the short side of the tumble flow contact area 50 is determined as follows. First, the opposing intake valve 32 and exhaust valve 34 are set as one set. In the system of the present embodiment, two sets of intake valves 32 and exhaust valves 34 are arranged side by side.
- the umbrella portions of both valves are projected onto the crown surface 35 for each set.
- Parallel lines are drawn for the two sets.
- the distance between the parallel line segments is determined as the short side of the tumble flow contact region 50.
- the tumble flow contact region 50 is defined in a band shape as a range sandwiched between the parallel line segments on the crown surface 35.
- the amount of heat received from the combustion gas to the piston 16 is determined by setting the region 52 where a strong air flow is not applied during the intake stroke as a heat insulating region. Can be reduced, and cooling loss can be reduced.
- the tumble flow contact region 50 where a strong tumble flow hits during the intake stroke is a region having a high heat transfer rate
- the tumble flow contact region 50 is a non-adiabatic region.
- the temperature of the tumble flow contact region 50 can be reduced as compared with the case where the heat insulating layer is formed.
- the amount of intake gas heated by the piston crown surface can be reduced.
- the temperature of the intake gas at the compression end is reduced, and knocking can be suppressed.
- the short side of the tumble flow contact region 50 is drawn for each group by drawing a line segment connecting the centers of the projected umbrella portions of both valves.
- the method of determining the short side of the tumble flow contact region 50 is not limited to this.
- a tangent on the piston center side is drawn among the projected common tangents of the umbrella portions of both valves, and the distance between the parallel tangents drawn for each set is expressed as a tumble flow contact region 50. It may be determined as the short side of.
- a tangent on the piston outer edge side is drawn out of the common tangent of the umbrella portion of both valves projected for each set, and the distance of the parallel tangent drawn for each set is expressed as a tumble flow contact region. It may be determined as 50 short sides. This also applies to the following embodiments.
- a port injection type injector is used as the injector, but an in-cylinder direct injection type injector may be used. This also applies to the following embodiments.
- the piston 16 is the “piston” in the first and second inventions
- the crown surface 35 is the “piston crown” in the first and second inventions.
- the contact area 50 corresponds to the “non-insulating area” in the first and second inventions
- the area 52 corresponds to the “insulating area” in the first and second inventions.
- Embodiment 2 FIG. (Basic configuration) Next, a second embodiment of the present invention will be described with reference to FIGS. 3 (A) and 3 (B).
- the system of this embodiment is substantially the same as the configuration shown in FIG. 1 except that a piston 60 described later is used instead of the piston 16 in the configuration shown in FIG.
- FIG. 3A is a top view showing the structure of the crown surface 62 of the piston 60 in the system of the present embodiment.
- valve recesses 64 IN corresponding to the umbrella portions of the two intake valves 32 are formed on the crown surface 62 of the piston 60.
- valve recesses 64 EX corresponding to the umbrella portions of the two exhaust valves 34 are formed on the crown surface 62.
- the crown surface 35 is formed with two outer edge portions 66 forming a squish area with the valve recesses 64 IN and 64 EX interposed therebetween.
- FIG. 3 (B) is a longitudinal sectional view of the piston 60 along the C surface shown in FIG. 3 (A).
- a piston pin boss 68 is provided below the piston 60.
- the piston pin bosses 68 are respectively provided on the side portions of the crown surface 62 that are positioned perpendicular to the intake-exhaust direction.
- the piston pin 18 shown in FIG. 1 is inserted into the piston pin boss 68.
- an intake air flow (hereinafter referred to as an intake gas flow composed of a mixture of fuel and fresh air) in the system of the present embodiment will be described.
- an intake gas flow composed of a mixture of fuel and fresh air
- a tumble flow indicated by solid arrows a1 to a3 is formed as in FIG.
- the arrow a3 shown in FIG. 3A indicates the flow of the intake gas that comes into contact with the crown surface 62 in the intake stroke, like the solid arrow a3 in FIG.
- a region 70 on the crown surface 62 shown in FIG. 3A represents a region where the intake gas as a tumble flow flows in contact with the crown surface 62.
- the region 70 is referred to as a tumble flow contact region.
- FIG. 3A shows an elliptical tumble flow contact region 70 that includes the central portion of the piston 60 and has a long side in the direction in which the intake air flows.
- a tumble flow is formed in the intake stroke.
- the intake flow that is a tumble flow flows from the exhaust side of the cylinder 14 toward the crown surface 62 of the piston 60 and passes toward the intake side of the cylinder 14 while contacting the crown surface 62. Therefore, a strong air current hits the tumble flow contact area 70 of the crown surface 62.
- At least the tumble flow contact area 70 where a strong air current hits is set as a non-insulated area without a heat insulating layer.
- the portion other than the tumble flow contact region 70 on the crown surface 62 is also configured as a non-insulating region.
- a heat insulating material 72 is inserted so as to be buried in a shallow position from the crown surface 62 inside the piston 60 as shown in FIG.
- the heat insulating material 72 is provided at the boundary between the tumble flow contact region 70 and the other regions in the top view of the piston.
- the heat insulating material 72 is provided in two locations in parallel to the flow of the intake air flow.
- the heat insulating material 72 is a rectangular parallelepiped, for example, it is not limited to this.
- a member having a heat insulating effect such as ceramic is used.
- the heat insulating material 72 shown in FIG. 3B is inside the piston 60 above the piston pin boss 68, and is perpendicular to the axial direction of the piston pin boss 68 (the axial direction of the piston pin 18), and the crown surface 62. It is provided in parallel with.
- the tumble flow contact region 70 where a strong tumble flow hits during the intake stroke is a region having a high heat transfer coefficient. Since heat conductivity is high, heat moves from the piston 60 to the intake gas. Therefore, the temperature of the tumble flow contact area 70 is lowered. At this time, since the portion other than the tumble flow contact region 70 is at a high temperature, the heat moves to the tumble flow contact region 70 whose temperature has been lowered and tries to maintain equilibrium.
- the heat transfer can be blocked by inserting the heat insulating material 72.
- the temperature of the tumble flow contact region 70 where the strong tumble flow strikes can be kept low. Therefore, the amount of heating to the intake gas can be reduced. As a result, the temperature of the intake gas at the compression end is reduced, and knocking can be suppressed. Therefore, according to the present invention, knocking can be suppressed in the internal combustion engine in which a tumble flow is formed in the cylinder.
- the heat insulating material 72 is provided in two locations in the piston 60 in parallel to the flow of the intake air flow, but the arrangement of the heat insulating material 72 is limited to this. It is not a thing. For example, it may be provided so as to surround the entire outer periphery of the tumble flow contact region 70 or a part thereof.
- the non-insulating region of the crown surface 62 is the entire crown surface 62, but the region other than the tumble flow contact region 70 is a heat insulating region in which a heat insulating layer is formed. It is good.
- the piston 60 is the “piston” in the third and fourth inventions
- the crown surface 62 is the “piston crown” in the third and fourth inventions
- the heat insulating material includes the tumble flow contact region 70 in the “heat insulating member” in the third and fourth inventions, and the tumble flow contact region 70 in the “tumble flow contact region” in the third invention.
- the upper region corresponds to the “non-insulating region” in the third and fourth inventions
- the piston pin boss 68 corresponds to the “piston pin boss” in the fourth invention.
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- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Pistons, Piston Rings, And Cylinders (AREA)
- Combustion Methods Of Internal-Combustion Engines (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
Description
吸気行程中に前記タンブル流が当接するピストン冠面上の領域であり、断熱層を有さない非断熱領域と、
前記非断熱領域以外の前記ピストン冠面上の少なくとも一部の領域であり、断熱層を有する断熱領域と、を備えることを特徴とする。
ピストン冠面の中央部を含み、該ピストン冠面の吸気側と排気側とに渡って帯状に設けられた、断熱層を有さない非断熱領域と、
前記非断熱領域の側方にあたる前記ピストン冠面に設けられた、断熱層を有する断熱領域と、を備えることを特徴とする。
ピストン冠面上に設けられ、吸気行程中に前記タンブル流が当接するタンブル流当接領域を少なくとも含む、断熱層を有さない非断熱領域と、
前記タンブル流当接領域の周辺部のピストン内部に設けられた断熱部材と、を備えることを特徴とする。
少なくともピストン冠面の中央部を含む該ピストン冠面に設けられた、断熱層を有さない非断熱領域と、
ピストンピンボスの上部に位置するピストン内部であり、該ピストンピンボスの軸方向に垂直かつ、前記ピストン冠面に平行に設けられた断熱部材と、を備えることを特徴とする。
12 シリンダブロック
14 気筒
16、60 ピストン
18 ピストンピン
20 コネクティングロッド
22 シリンダヘッド
24 燃焼室
26 点火プラグ
28 吸気ポート
30 排気ポート
32 吸気バルブ
34 排気バルブ
35、62 冠面
36 中央部
38、66 ピストン冠面の外縁部
40 シリンダヘッドの下面凹部の外縁部
42 燃焼室の上面部
44 気筒の排気側の側壁
46 気筒の吸気側の側壁
48EX、48IN、64IN、64EX バルブリセス
50、70 タンブル流当接領域
52 タンブル流当接領域以外の領域
68 ピストンピンボス
72 断熱材
(基本的構成)
図1は、本発明の実施の形態1における内燃機関10のシステム構成を説明するための図である。本実施形態のシステムは、内燃機関10を備えている。ここでは、内燃機関10は4サイクルエンジンであるものとする。図1には、内燃機関10の縦断面が表されている。
次に、本実施形態のシステムにおける吸気流(以下、燃料と新気との混合気からなる吸気ガスの流れをいう。)について説明する。図1には、本実施形態のシステムの吸気行程において、気筒14内に形成される吸気流の代表的な流れが示されている。実線の矢印a1は、吸気行程において、吸気ポート28から吸入され、吸気ポート28側に面する吸気バルブ32の傘裏面に沿って、燃焼室24の上面部42に導かれる吸気ガスの流れを示している。実線の矢印a2は、吸気行程において、燃焼室24の上面部42から燃焼室24に面する排気バルブ34の傘表面に沿って、気筒14の排気側の側壁44に導かれる吸気ガスの流れを示している。実線の矢印a3は、吸気行程において、気筒14の排気側の側壁44から冠面35に当接して、気筒14の吸気側の側壁46に導かれる吸気ガスの流れを示している。このように、本実施形態のシステムでは、実線の矢印a1~a3に示すタンブル流が形成される。実線の矢印a3の方向はピストンピン18の軸線に対し垂直である。
(基本的構成)
次に、図3(A)、図3(B)を参照して本発明の実施の形態2について説明する。本実施形態のシステムは図1に示す構成におけるピストン16に代えて、後述するピストン60が用いられる点を除き、図1に示す構成と略同様である。
次に、本実施の形態のシステムにおける吸気流(以下、燃料と新気との混合気からなる吸気ガスの流れをいう。)について説明する。本実施形態のシステムでは、上述した図1と同様に、実線の矢印a1~a3に示すタンブル流が形成される。
Claims (4)
- 気筒内にタンブル流が形成される内燃機関のピストンにおいて、
吸気行程中に前記タンブル流が当接するピストン冠面上の領域であり、断熱層を有さない非断熱領域と、
前記非断熱領域以外の前記ピストン冠面上の少なくとも一部の領域であり、断熱層を有する断熱領域と、
を備えることを特徴とする内燃機関のピストン。 - ピストン冠面の中央部を含み、該ピストン冠面の吸気側と排気側とに渡って帯状に設けられた、断熱層を有さない非断熱領域と、
前記非断熱領域の側方にあたる前記ピストン冠面に設けられた、断熱層を有する断熱領域と、
を備えることを特徴とする内燃機関のピストン - 気筒内にタンブル流が形成される内燃機関のピストンにおいて、
ピストン冠面上に設けられ、吸気行程中に前記タンブル流が当接するタンブル流当接領域を少なくとも含む、断熱層を有さない非断熱領域と、
前記タンブル流当接領域の周辺部のピストン内部に設けられた断熱部材と、
を備えることを特徴とする内燃機関のピストン。 - 少なくともピストン冠面の中央部を含む該ピストン冠面に設けられた、断熱層を有さない非断熱領域と、
ピストンピンボスの上部に位置するピストン内部であり、該ピストンピンボスの軸方向に垂直かつ、前記ピストン冠面に平行に設けられた断熱部材と、
を備えることを特徴とする内燃機関のピストン。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
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PCT/JP2010/052159 WO2011099156A1 (ja) | 2010-02-15 | 2010-02-15 | 内燃機関のピストン |
JP2011553700A JP5293842B2 (ja) | 2010-02-15 | 2010-02-15 | 内燃機関のピストン |
DE112010005268.9T DE112010005268B4 (de) | 2010-02-15 | 2010-02-15 | Kolben für Maschine mit interner Verbrennung |
CN201080063877.5A CN102762836B (zh) | 2010-02-15 | 2010-02-15 | 内燃机的活塞 |
US13/578,968 US8978611B2 (en) | 2010-02-15 | 2010-02-15 | Piston for internal combustion |
Applications Claiming Priority (1)
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PCT/JP2010/052159 WO2011099156A1 (ja) | 2010-02-15 | 2010-02-15 | 内燃機関のピストン |
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PCT/JP2010/052159 WO2011099156A1 (ja) | 2010-02-15 | 2010-02-15 | 内燃機関のピストン |
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US (1) | US8978611B2 (ja) |
JP (1) | JP5293842B2 (ja) |
CN (1) | CN102762836B (ja) |
DE (1) | DE112010005268B4 (ja) |
WO (1) | WO2011099156A1 (ja) |
Families Citing this family (5)
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CN104696066A (zh) * | 2014-01-18 | 2015-06-10 | 摩尔动力(北京)技术股份有限公司 | 大绝热指数发动机 |
EP3440230B1 (en) * | 2016-04-08 | 2020-01-08 | Volvo Truck Corporation | A piston for a cylinder for an internal combustion engine |
US11022027B2 (en) * | 2016-11-18 | 2021-06-01 | Honda Motor Co., Ltd. | Internal combustion engine with reduced engine knocking |
JP6733811B2 (ja) | 2017-04-04 | 2020-08-05 | 日産自動車株式会社 | ピストン |
CN114107874A (zh) * | 2022-01-27 | 2022-03-01 | 潍柴动力股份有限公司 | 一种隔热活塞及制备方法 |
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- 2010-02-15 JP JP2011553700A patent/JP5293842B2/ja not_active Expired - Fee Related
- 2010-02-15 CN CN201080063877.5A patent/CN102762836B/zh not_active Expired - Fee Related
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Also Published As
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DE112010005268T5 (de) | 2013-02-28 |
CN102762836B (zh) | 2014-08-27 |
JP5293842B2 (ja) | 2013-09-18 |
US8978611B2 (en) | 2015-03-17 |
JPWO2011099156A1 (ja) | 2013-06-13 |
DE112010005268B4 (de) | 2019-07-04 |
CN102762836A (zh) | 2012-10-31 |
US20120318230A1 (en) | 2012-12-20 |
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