WO2011135720A1 - エンジンのピストン - Google Patents
エンジンのピストン Download PDFInfo
- Publication number
- WO2011135720A1 WO2011135720A1 PCT/JP2010/057692 JP2010057692W WO2011135720A1 WO 2011135720 A1 WO2011135720 A1 WO 2011135720A1 JP 2010057692 W JP2010057692 W JP 2010057692W WO 2011135720 A1 WO2011135720 A1 WO 2011135720A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- engine
- combustion chamber
- piston
- dead center
- top dead
- Prior art date
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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
- F02F3/00—Pistons
- F02F3/26—Pistons having combustion chamber in piston head
-
- 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
-
- 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
-
- 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
- F02B2275/00—Other engines, components or details, not provided for in other groups of this subclass
- F02B2275/48—Tumble motion in gas movement in cylinder
-
- 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 an engine piston, and more particularly to an engine piston for a multi-cylinder engine in which a swirling airflow is generated in a combustion chamber.
- Patent Document 1 discloses a technique that is considered to be related to the present invention in that it is a technique related to an engine that generates a tumble flow.
- Patent Document 2 or 3 discloses a technique that discloses a structure that is considered to be related to the present invention for a piston.
- JP 2007-46457 A Japanese Patent Application Laid-Open No. 11-2000946 Japanese Utility Model Publication No. 05-38342
- the temperature of the wall portion formed between the cylinders is particularly likely to rise due to the structure.
- the temperature of the wall portion formed between the cylinders shown in (a) is compared with the temperature of the cylinder wall portion formed on the engine intake side shown in (b). High in all engine operating conditions. Further, when the engine operating state changes from the low rotation and low load operation region to the high rotation and high load operation region, the temperature shown in (a) is larger than the temperature shown in (b). It is getting higher.
- the temperature rise of the wall portion formed between the cylinders may cause abnormal consumption of engine oil, and there is a concern that this may occur during high-speed high-load operation particularly in an engine that performs high-speed combustion.
- Such a temperature rise has a problem in that it may hinder the improvement of fuel consumption, particularly in an engine that performs high-speed combustion to improve fuel consumption.
- an object of the present invention is to provide an engine piston capable of suitably suppressing a temperature rise of a wall portion formed between cylinders of a multi-cylinder engine.
- the present invention for solving the above-described problems is used in a multi-cylinder engine in which a swirling airflow is generated in a combustion chamber, and a top ring groove and an upper surface outer peripheral portion at a position facing an adjacent cylinder in the multi-cylinder engine.
- a swirling airflow is generated in a combustion chamber, and a top ring groove and an upper surface outer peripheral portion at a position facing an adjacent cylinder in the multi-cylinder engine.
- the combustion chamber at the position facing the top ring groove at the top dead center until at least the position where the amount of heat transfer in the combustion chamber exceeds the maximum after the compression stroke top dead center. And a portion formed into a raised shape so as not to expose the bore wall surface.
- the swirling airflow is a tumble flow
- the compression stroke is performed at least after the compression stroke top dead center until the heat transfer amount in the combustion chamber exceeds the highest position.
- the crank angle is between the compression stroke top dead center and a predetermined angle included in the range of 30 ° to 50 °.
- the temperature rise of the wall portion formed between the cylinders of the multi-cylinder engine can be suitably suppressed.
- FIG. 4 is a cross-sectional view of the engine piston taken along line AA in FIG. 3. It is explanatory drawing about the piston of an engine. It is a figure which shows the movement amount of the heat
- An engine 50 shown in FIGS. 1 and 2 is an in-line four-cylinder multi-cylinder engine.
- a piston hereinafter simply referred to as a piston
- the cylinder block 51 is formed with a plurality of (here, four) cylinders 51a and a water jacket 51b.
- a wall portion 51c is formed between adjacent cylinders among the plurality of cylinders 51a.
- the piston 1 is accommodated in the cylinder 51a.
- a cylinder head 52 is fixed to the upper surface of the cylinder block 51.
- the combustion chamber 53 is formed as a space surrounded by the piston 1, the cylinder block 51 and the cylinder head 52.
- the cylinder head 52 has an intake port 52a and an exhaust port 52b.
- the intake port 52 a guides the intake air S to the combustion chamber 53, and the exhaust port 52 b exhausts the gas in the combustion chamber 53.
- the intake port 52 a serves as an intake introduction means for introducing intake air so as to generate a swirling air flow in the combustion chamber 53, and the intake air S introduced into the combustion chamber 53 forms a tumble flow T.
- a tumble flow having a high tumble ratio with a tumble ratio (the number of times the tumble flow T rotates while the piston 1 reciprocates once) is approximately 2.0 is generated as the tumble flow T.
- the cylinder head 52 is provided with intake and exhaust valves 55 and 56 for opening and closing these intake and exhaust ports 52a and 52b.
- the cylinder head 52 is provided with a spark plug 57 with an electrode protruding substantially at the center of the upper portion of the combustion chamber 53.
- the piston 1 includes a cavity 2 for guiding the tumble flow T on the upper surface.
- the cavity 2 is provided in the combustion chamber 53 so as to guide the tumble flow T along the direction connecting the intake side and the exhaust side.
- a plurality (three in this case) of ring grooves are formed on the outer periphery of the piston 1.
- the ring groove provided at the position closest to the upper surface is the top ring groove 3.
- Each of the piston rings (not shown) provided in the ring groove including the top ring groove 3 has a function of scraping off oil on the wall surface of the cylinder 51a which is a bore wall surface and a function of keeping the combustion chamber 53 airtight.
- a pin boss hole 4 is formed in the piston 1.
- the portions 10 positioned at both ends in the extending direction of the pin boss hole 4 are not formed in a uniform plane but are formed in a raised shape.
- the portion 10 is formed in a raised shape so as to gradually rise from both sides of the intake side and the exhaust side.
- At least one of the portions 10 is a portion disposed at a position facing an adjacent cylinder in the engine 50. That is, at least one of the portions 10 is a portion disposed at a position facing the wall portion 51c.
- the portion 10 is further formed in the combustion chamber 53 as shown below.
- the piston 1 when the crank angle is 40 ° ATDC is indicated by a solid line
- the piston 1 when located at the top dead center is indicated by a broken line.
- a position P indicates the position of the wall surface of the cylinder 51a facing the top ring groove 3 at the top dead center.
- the portion 10 reaches the position P until the heat flux indicating the heat transfer amount in the combustion chamber 53 reaches the highest position after the compression stroke top dead center, and reaches the position P until the wall of the cylinder 51 a is reached. It is formed in a raised shape so as not to be exposed.
- the portion 51ca below the position P of the wall portion 51c facing the portion 10 is a portion that needs to suppress the temperature rise particularly in order to suppress the occurrence of abnormal oil consumption due to oil rising. It has become.
- the heat flux specifically changes as shown in FIG. As shown in FIG. 6, the heat flux rapidly increases after the top dead center of the compression stroke, and then decreases with a peak. In this respect, specifically, the heat flux becomes the highest when the crank angle becomes approximately 25 ° ATDC, and thereafter becomes zero when the crank angle becomes approximately 50 ° ATDC.
- the portion 51ca is not exposed in a state where such heat flux is generated, the temperature rise of the portion 51ca due to the flame or combustion gas coming into contact with the portion 51ca can be suppressed.
- the crank angle is between the top dead center of the compression stroke and the predetermined angle included in the range from 30 ° to 50 ° (in the range from 30 ° ATDC to 50 ° ATDC). Is preferred.
- the predetermined angle by setting the predetermined angle to 30 °, the partial heat zone (between 20 ° ATDC and 30 ° ATDC) in which the heat flux is particularly high before and after the peak value in the heat flux shown in FIG. Portion) can be included in the range R of the crank angle that suppresses heat transfer to the portion 51ca.
- the predetermined angle by setting the predetermined angle to 50 °, the heat flux shown in FIG.
- the portion 10 when the portion 10 is formed in a larger and raised shape, the weight of the piston 1 is increased correspondingly, and the strength of the portion 10 may be affected.
- the heat flux increases mainly up to 40 ° ATDC as shown in FIG.
- the predetermined angle by setting the predetermined angle to 40 °, heat transfer to the portion 51ca can be further suppressed as compared with the case where the predetermined angle is 30 °, and at the same time, the portion 10 is made smaller than when the predetermined angle is 50 °. can do.
- the heat flux further changes as shown in FIG. 7 according to the tumble ratio.
- the crank angle at which the heat flux peak is formed gradually moves away from the top dead center of the compression stroke as the tumble ratio (TR) decreases.
- the peak value of the heat flux gradually decreases as the tumble ratio decreases.
- the tumble ratio is not only the case where the tumble ratio is a high tumble ratio (specifically, approximately 2.0 here) (in the case of T1), but the tumble ratio is the medium tumble ratio. (Specifically about 1.2 here) (T2), or when the tumble ratio is low tumble ratio (specifically about 0.5 here) (T3).
- the heat flux peak can be included in the range R.
- the predetermined angle is set to 40 °, especially in the case of T2, the heat transfer to the portion 51ca can be suitably suppressed in combination with the decrease in the peak value of the heat flux. For this reason, when the predetermined angle is set to 40 °, the compatibility with a wide tumble ratio including a high tumble ratio can be preferably improved.
- the crank angle at which the peak of heat flux is formed gradually approaches the top dead center of the compression stroke as the tumble ratio increases.
- the peak value of the heat flux gradually increases as the tumble ratio increases.
- the predetermined angle is set to an angle smaller than 40 ° according to the tumble ratio, so that the heat transfer is performed to the same extent as when the predetermined angle is set to 40 °. While suppressing, it is possible to further reduce the size of the portion 10 as compared with the case where the predetermined angle is set to 40 °.
- the tumble ratio is lower than 2.0, the peak value of the heat flux is reduced as compared with the case where the tumble ratio is 2.0, but the predetermined angle is larger than 40 ° according to the tumble ratio.
- the angle By setting the angle, heat transfer can be further suppressed as compared with the case where the predetermined angle is 40 °.
- the tumble flow T is generated as a swirling air flow in the combustion chamber 53, and the generated swirling air flow is maintained until the latter half of the compression stroke and collapsed, thereby disturbing the atmosphere in the combustion chamber 53.
- High-speed combustion is performed by improving the combustion speed.
- the temperature of the combustion gas increases due to the improvement of the combustion speed, and the temperature boundary layer becomes thin due to the swirling airflow.
- the heat transfer coefficient increases, so the combustion chamber 53 The wall temperature becomes higher.
- the amount of heat generated per unit time increases and the strength of the swirl airflow increases to further increase the heat transfer coefficient.
- the temperature rise of the wall portion 51c is particularly problematic in such circumstances.
- the piston 1 that can suppress the temperature rise of the portion 51ca as described above is suitable for the engine 50 that generates a swirling airflow in the combustion chamber 53 and performs high-speed combustion.
- the intake air introduction means is the intake port 52a
- the present invention is not necessarily limited to this, and the intake air introduction means is realized, for example, by an airflow control valve that is provided in the intake port and can control the flow of intake air, or a combination of the airflow control valve and the intake port. May be.
- the swirling airflow is the tumble flow T
- the present invention is not necessarily limited to this, and the swirling airflow may be, for example, a swirl flow or an oblique tumble flow.
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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)
Abstract
Description
また部分10を形成するにあたっては、図6に示す熱流束の変化態様に鑑み、具体的には圧縮行程上死点後、少なくとも熱流束が最も高くなる位置を超えるまでの間を、圧縮行程上死点後、クランク角度が圧縮行程上死点を始点として30°から50°までの範囲内(30°ATDCから50°ATDCまでの範囲内)に含まれる所定角度を超えるまでの間とすることが好ましい。
この点、所定角度を40°とすることで、所定角度が30°の場合と比較してさらに部分51caへの熱移動を抑制でき、同時に所定角度が50°の場合よりも部分10を小型化することができる。
この点、上述のようにして部分51caの温度上昇を抑制できるピストン1は、燃焼室53内に旋回気流を生成し、高速燃焼を行うエンジン50に好適である。
例えば上述した実施例では吸気導入手段が吸気ポート52aである場合について説明した。しかしながら、本発明においては必ずしもこれに限られず、吸気導入手段は、例えば吸気ポート内に設けられ、吸気の流れを制御可能な気流制御弁や、気流制御弁と吸気ポートとの組み合わせなどによって実現されてもよい。
また例えば上述した実施例では旋回気流がタンブル流Tである場合について説明した。しかしながら、本発明においては必ずしもこれに限られず、旋回気流は例えばスワール流や斜めタンブル流などであってもよい。
3 トップリング溝
50 エンジン
51 シリンダブロック
51a シリンダ
52 シリンダヘッド
52a 吸気ポート
53 燃焼室
Claims (2)
- 燃焼室内に旋回気流が生成される多気筒エンジンに用いられ、
トップリング溝と、
上面外周部のうち、前記多気筒エンジンにおいて隣り合う気筒に対向する位置に配置されるとともに、前記燃焼室内において、圧縮行程上死点後、少なくとも前記燃焼室における熱の移動量が最も大きくなる位置を超えるまでの間、上死点において前記トップリング溝に対向する位置にまで至りボア壁面を露出させないように盛り上がった形状に形成された部分と、を有するエンジンのピストン。 - 請求項1記載のエンジンのピストンであって、
前記旋回気流がタンブル流であり、
前記部分を形成するにあたり、圧縮行程上死点後、少なくとも前記燃焼室における熱の移動量が最も高くなる位置を超えるまでの間を、圧縮行程上死点後、クランク角度が圧縮行程上死点を始点として30°から50°までの範囲内に含まれる所定角度を超えるまでの間としたエンジンのピストン。
Priority Applications (5)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
DE112010005533T DE112010005533T5 (de) | 2010-04-30 | 2010-04-30 | Kolben einer Kraftmaschine |
JP2012512608A JP5293886B2 (ja) | 2010-04-30 | 2010-04-30 | エンジンのピストン |
PCT/JP2010/057692 WO2011135720A1 (ja) | 2010-04-30 | 2010-04-30 | エンジンのピストン |
CN201080035103.1A CN102472199B (zh) | 2010-04-30 | 2010-04-30 | 发动机的活塞 |
US13/322,511 US20130047949A1 (en) | 2010-04-30 | 2010-04-30 | Piston of engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
PCT/JP2010/057692 WO2011135720A1 (ja) | 2010-04-30 | 2010-04-30 | エンジンのピストン |
Publications (1)
Publication Number | Publication Date |
---|---|
WO2011135720A1 true WO2011135720A1 (ja) | 2011-11-03 |
Family
ID=44861059
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
PCT/JP2010/057692 WO2011135720A1 (ja) | 2010-04-30 | 2010-04-30 | エンジンのピストン |
Country Status (5)
Country | Link |
---|---|
US (1) | US20130047949A1 (ja) |
JP (1) | JP5293886B2 (ja) |
CN (1) | CN102472199B (ja) |
DE (1) | DE112010005533T5 (ja) |
WO (1) | WO2011135720A1 (ja) |
Families Citing this family (1)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JP6897557B2 (ja) * | 2017-12-27 | 2021-06-30 | トヨタ自動車株式会社 | 内燃機関 |
Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2002295261A (ja) * | 2001-03-30 | 2002-10-09 | Mazda Motor Corp | 火花点火式直噴エンジン |
JP2003502550A (ja) * | 1999-06-09 | 2003-01-21 | エフ・エー・フアウ・モトーレンテヒニック・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング | 二次給気流発生手段を備えたピストン式内燃機関 |
JP2003120300A (ja) * | 2001-09-26 | 2003-04-23 | Hyundai Motor Co Ltd | ガソリン直接噴射式エンジン |
Family Cites Families (11)
Publication number | Priority date | Publication date | Assignee | Title |
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JP3233953B2 (ja) | 1991-08-07 | 2001-12-04 | オリンパス光学工業株式会社 | カテーテル装置 |
JPH08338274A (ja) * | 1995-06-09 | 1996-12-24 | Honda Motor Co Ltd | エンジンの燃焼制御装置 |
BR9601835A (pt) * | 1996-06-14 | 1998-09-29 | Metal Leve Sa | Embolo para motor de combustão interna |
JP3746344B2 (ja) * | 1996-12-24 | 2006-02-15 | トヨタ自動車株式会社 | 内燃機関の燃焼室構造 |
JP3835916B2 (ja) | 1998-01-13 | 2006-10-18 | 三菱重工業株式会社 | 肉盛強化ピストンの製造方法 |
JP4415497B2 (ja) * | 2000-03-29 | 2010-02-17 | マツダ株式会社 | 火花点火式直噴エンジン |
JP3991789B2 (ja) * | 2002-07-04 | 2007-10-17 | トヨタ自動車株式会社 | 混合気を圧縮自着火させる内燃機関 |
JP2007046457A (ja) | 2003-09-22 | 2007-02-22 | Toyota Motor Corp | 内燃機関の吸気ポートおよびその製造方法 |
CA2463791C (en) * | 2003-09-30 | 2012-01-03 | Westport Research Inc. | Method for injecting gaseous fuels into an internal combustion engine at high pressures |
US7484498B2 (en) * | 2006-03-31 | 2009-02-03 | Mazda Motor Corporation | Spark-ignition gasoline engine |
JP4254865B2 (ja) * | 2007-01-29 | 2009-04-15 | トヨタ自動車株式会社 | 内燃機関用ピストン及びそのピストンが適用された内燃機関 |
-
2010
- 2010-04-30 JP JP2012512608A patent/JP5293886B2/ja not_active Expired - Fee Related
- 2010-04-30 WO PCT/JP2010/057692 patent/WO2011135720A1/ja active Application Filing
- 2010-04-30 CN CN201080035103.1A patent/CN102472199B/zh not_active Expired - Fee Related
- 2010-04-30 DE DE112010005533T patent/DE112010005533T5/de not_active Withdrawn
- 2010-04-30 US US13/322,511 patent/US20130047949A1/en not_active Abandoned
Patent Citations (3)
Publication number | Priority date | Publication date | Assignee | Title |
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JP2003502550A (ja) * | 1999-06-09 | 2003-01-21 | エフ・エー・フアウ・モトーレンテヒニック・ゲゼルシヤフト・ミト・ベシユレンクテル・ハフツング | 二次給気流発生手段を備えたピストン式内燃機関 |
JP2002295261A (ja) * | 2001-03-30 | 2002-10-09 | Mazda Motor Corp | 火花点火式直噴エンジン |
JP2003120300A (ja) * | 2001-09-26 | 2003-04-23 | Hyundai Motor Co Ltd | ガソリン直接噴射式エンジン |
Also Published As
Publication number | Publication date |
---|---|
JP5293886B2 (ja) | 2013-09-18 |
US20130047949A1 (en) | 2013-02-28 |
CN102472199B (zh) | 2014-04-23 |
DE112010005533T5 (de) | 2013-05-16 |
JPWO2011135720A1 (ja) | 2013-07-18 |
CN102472199A (zh) | 2012-05-23 |
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