JP4586519B2 - Internal combustion engine - Google Patents

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JP4586519B2
JP4586519B2 JP2004352511A JP2004352511A JP4586519B2 JP 4586519 B2 JP4586519 B2 JP 4586519B2 JP 2004352511 A JP2004352511 A JP 2004352511A JP 2004352511 A JP2004352511 A JP 2004352511A JP 4586519 B2 JP4586519 B2 JP 4586519B2
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valve
intake
intake valve
lift
lift amount
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JP2006161632A (en
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亮介 日吉
毅 有永
晋 石崎
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Nissan Motor Co Ltd
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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

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  • Combustion Methods Of Internal-Combustion Engines (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Output Control And Ontrol Of Special Type Engine (AREA)
  • Electrical Control Of Air Or Fuel Supplied To Internal-Combustion Engine (AREA)

Description

本発明は、機関負荷に応じて吸気弁のバルブリフト量を変更可能な内燃機関に関する。   The present invention relates to an internal combustion engine capable of changing a valve lift amount of an intake valve in accordance with an engine load.

吸気弁のバルブリフト特性を機関運転状態に応じて可変制御する内燃機関の可変動弁装置が特許文献１等により従来より知られている。
特開２００２−８９３０３号公報 A variable valve operating apparatus for an internal combustion engine that variably controls the valve lift characteristic of the intake valve in accordance with the engine operating state is conventionally known from Patent Document 1 and the like.
JP 2002-89303 A

ところで、スロットル開度と吸気弁のバルブリフト量とを制御することによってエンジン負荷を制御する場合、スロットル下流に吸入負圧が発生するためポンピング損失が増大し燃費が悪化するという問題がある。これを解決するためにノンスロットルとし、吸気弁のバルブリフト量を精密制御することによってポンピング損失を低減し燃費を向上する方法がある。しかし、吸気弁のバルブリフト量を制御することで安定した負荷制御を行うためには、吸気弁極小リフト時における吸気弁のバルブリフト量の精密な制御が必要となる。つまり、可変動弁装置の製造時における気筒間及び各気筒毎での吸気弁のバルブリフト量のばらつき幅を小さくすることによって気筒間吸入空気量ばらつき幅を小さくする必要があり、製造コストが増大するという問題があった。   By the way, when the engine load is controlled by controlling the throttle opening and the valve lift amount of the intake valve, there is a problem that the pumping loss increases and the fuel consumption deteriorates because the suction negative pressure is generated downstream of the throttle. In order to solve this problem, there is a method of reducing the pumping loss and improving the fuel consumption by using non-throttle and precisely controlling the valve lift amount of the intake valve. However, in order to perform stable load control by controlling the valve lift amount of the intake valve, precise control of the valve lift amount of the intake valve at the time of the intake valve minimum lift is required. In other words, it is necessary to reduce the variation range of the intake air amount between cylinders by reducing the variation range of the valve lift amount of the intake valve between the cylinders and for each cylinder at the time of manufacturing the variable valve operating device, which increases the manufacturing cost. There was a problem to do.

本発明は、このような従来の問題点に着目してなされたもので、吸気弁極小リフト時の吸気弁のバルブリフト量のばらつきによって生じる吸入空気量のばらつき幅を低減することによって、吸気弁のバルブリフト量ばらつき許容値を拡大し可変動弁装置の製造コストを低減することを目的としている。   The present invention has been made paying attention to such a conventional problem, and by reducing the variation range of the intake air amount caused by the variation of the valve lift amount of the intake valve at the time of the intake valve minimal lift, the intake valve is reduced. It is intended to reduce the manufacturing cost of the variable valve operating device by expanding the allowable valve lift amount variation.

そこで、本発明は、機関負荷に応じて吸気弁のバルブリフト量を変更可能な内燃機関において、吸気弁のバルブシートの外周側の燃焼室壁面には、吸気弁のバルブリフト量が極小リフトとなる運転状態時における吸入空気量が相対的に減少するよう、吸気弁のバルブリフト量が極小リフトとなる運転状態時の吸気弁最大リフト量よりも高く、かつ吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも低くなる第１壁部が、吸気弁のバルブシートの外周を全周に亙って囲むように形成されていることを特徴としている。これによって、吸気弁極小リフト時における吸入空気量が相対的に減少し、吸気弁開口面積の変化によって変わる吸入空気量の変化が小さくなって、吸気弁極小リフト時の吸入空気量のバラツキが低減されることになる。
Accordingly, the present invention provides an internal combustion engine capable of changing the valve lift amount of the intake valve in accordance with the engine load, and the valve lift amount of the intake valve is a minimum lift on the combustion chamber wall surface on the outer peripheral side of the valve seat of the intake valve. The valve lift amount of the intake valve is higher than the intake valve maximum lift amount during the operation state where the intake valve is minimally lifted, and the valve lift amount of the intake valve is a small lift so that the intake air amount in the operation state becomes relatively small. The first wall portion that is lower than the maximum lift amount of the intake valve in the operating state is formed so as to surround the outer periphery of the valve seat of the intake valve over the entire periphery . As a result, the intake air amount at the time of the intake valve minimum lift is relatively reduced, the change in the intake air amount that changes due to the change in the intake valve opening area is reduced, and the variation in the intake air amount at the time of the intake valve minimum lift is reduced. Will be.

本発明によれば、吸気弁の極小リフト時のリフトばらつき幅の許容範囲を拡大可能となり、製造後に吸気弁のリフトばらつきを低減するために行う必要があった部品の選別行程を、省略または簡素化することが可能になるため、コストを削減することが可能になる。   According to the present invention, it is possible to expand the allowable range of lift variation width at the time of the minimum lift of the intake valve, omitting or simplifying the part selection process that was necessary to reduce the lift variation of the intake valve after manufacture. Therefore, the cost can be reduced.

本発明の一実施形態を図面に基づいて詳細に説明する。尚、以下に説明する各実施形態は、機関負荷に応じて吸気弁のバルブリフト量を連続的に可変可能な可変動弁機構を備える内燃機関を前提とするものであり、低負荷時には吸気弁のバルブリフト量が高負荷時よりも小さくなるように制御され、アイドル運転時にはリフト量がさらに小さくなるように制御される。また、吸気弁のバルブリフト量を極小リフト域で制御することによって、スロットル開度の精密な制御を行うことなくエンジン負荷制御を行うこともできる。尚、吸気弁のバルブリフト特性を可変可能な可変動弁機構としては、本出願人が先に提案した特開平１１−１０７７２５号公報等によって既に公知となっているので、その構成についての詳細な説明は省略する。   An embodiment of the present invention will be described in detail with reference to the drawings. Each embodiment described below is based on an internal combustion engine including a variable valve mechanism that can continuously vary the valve lift amount of the intake valve according to the engine load. The valve lift amount is controlled to be smaller than that during high load, and the lift amount is controlled to be even smaller during idle operation. Further, by controlling the valve lift amount of the intake valve in the minimum lift region, it is possible to perform engine load control without performing precise control of the throttle opening. The variable valve mechanism that can change the valve lift characteristic of the intake valve is already known from Japanese Patent Application Laid-Open No. 11-107725 previously proposed by the present applicant. Description is omitted.

通常、吸気弁のバルブリフト量が極小リフト時には吸気流が吸気弁と吸気弁が着座するバルブシートとのわずかな隙間から、バルブシート周りの燃焼室壁面に接する方向に流れる。一方、吸気弁のバルブリフト量が小リフト時には極小リフト時よりもバルブリフト量が大きく、吸気流は吸気ポート壁面、吸気弁のバルブヘッド上面、バルブシート面方向に沿って流れるようになり、吸気流は極小リフト時とは異なり燃焼室壁面から剥離する。本発明では、小リフト時の吸気行程においては吸気流が筒内に円滑に流れるが、極小リフト時の吸気行程においては吸気流の筒内への流れが乱されるように吸気弁、排気弁、燃焼室、ピストン、バルブシートが構成される。   Normally, when the valve lift amount of the intake valve is a minimum lift, the intake flow flows in a direction in contact with the combustion chamber wall around the valve seat through a slight gap between the intake valve and the valve seat on which the intake valve is seated. On the other hand, when the valve lift amount of the intake valve is small, the valve lift amount is larger than that of the minimum lift, and the intake flow flows along the intake port wall surface, the intake valve valve head upper surface, and the valve seat surface direction. The flow separates from the wall of the combustion chamber, unlike during the minimal lift. In the present invention, the intake flow smoothly flows into the cylinder during the intake stroke at the time of the small lift, but the intake valve and the exhaust valve so that the flow of the intake flow into the cylinder is disturbed at the intake stroke at the time of the minimum lift. Combustion chamber, piston and valve seat are configured.

図１は、本発明の第１実施形態における内燃機関を模式的に示した説明図であって、ピストン側から見た内燃機関の燃焼室形状、換言すればシリンダヘッド側の燃焼室形状を示す説明図である。   FIG. 1 is an explanatory view schematically showing the internal combustion engine according to the first embodiment of the present invention, showing the shape of the combustion chamber of the internal combustion engine viewed from the piston side, in other words, the shape of the combustion chamber on the cylinder head side. It is explanatory drawing.

シリンダヘッド１には、機関負荷に応じてバルブリフト量が可変となるよう開閉制御される吸気弁２が一気筒当たり２つ配置されていると共に、排気弁３が一気筒当たり２つ配置されている。   The cylinder head 1 is provided with two intake valves 2 that are controlled to open and close so that the valve lift amount is variable according to the engine load, and two exhaust valves 3 are arranged per cylinder. Yes.

吸気弁２及び排気弁３は、ペントルーフ型の燃焼室４（後述の図２及び図３を参照））の上部壁面５にそれぞれ配置された吸気弁用バルブシート６び排気弁用バルブシート７に着座する。   The intake valve 2 and the exhaust valve 3 are respectively connected to an intake valve valve seat 6 and an exhaust valve valve seat 7 arranged on an upper wall surface 5 of a pent roof type combustion chamber 4 (see FIGS. 2 and 3 to be described later). Sit down.

吸気弁用バルブシート６は、シリンダヘッド１に形成された吸気ポート８（後述の図２及び図３を参照）と燃焼室４との接続部分に設けられている。排気弁用バルブシート７は、シリンダヘッド１に形成された排気ポート９（後述の図２及び図３を参照）と燃焼室４との接続部分に設けられている。   The intake valve valve seat 6 is provided at a connection portion between an intake port 8 (see FIGS. 2 and 3 described later) formed in the cylinder head 1 and the combustion chamber 4. The exhaust valve valve seat 7 is provided at a connection portion between an exhaust port 9 (see FIGS. 2 and 3 described later) formed in the cylinder head 1 and the combustion chamber 4.

そして、燃焼室４の上部壁面５には、吸気弁用バルブシート６の外周側を全周に亙って囲む第１壁部としての壁部１０が、各吸気弁２毎に形成されている。   The upper wall surface 5 of the combustion chamber 4 is formed with a wall portion 10 as a first wall portion surrounding the outer peripheral side of the intake valve valve seat 6 over the entire circumference for each intake valve 2. .

図２及び図３は、図１のＡ−Ａ線に沿った断面図であり、図２は吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態を示し、図３は吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転を除く低負荷運転状態を示している。   2 and 3 are cross-sectional views taken along the line AA in FIG. 1. FIG. 2 shows the idle operation state after warm-up in which the valve lift amount of the intake valve 2 is a minimum lift, and FIG. The low load operation state excluding the idle operation after warm-up in which the valve lift amount of the valve 2 is a small lift is shown.

そして、図２及び図３からも明らかなように、吸気弁２のバルブヘッド１１の側面１１ａと対向する壁部１０の壁面１０ａの高さＭ、すなわち壁部１０のバルブリフト方向への突き出し量Ｍは、吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態時における吸気弁２の最大リフト量Ｐｍａｘよりも高く、かつ吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転を除く低負荷運転状態時における吸気弁２の最大リフト量Ｒｍａｘよりも低くなるように形成されている。尚、図１中の１２は点火プラグである。   2 and 3, the height M of the wall surface 10a of the wall 10 facing the side surface 11a of the valve head 11 of the intake valve 2, that is, the protrusion amount of the wall 10 in the valve lift direction. M is higher than the maximum lift amount Pmax of the intake valve 2 in the idle operation state after warm-up when the valve lift amount of the intake valve 2 is a minimum lift, and warm-up when the valve lift amount of the intake valve 2 is a small lift It is formed to be lower than the maximum lift amount Rmax of the intake valve 2 in the low load operation state excluding the post-idle operation. In addition, 12 in FIG. 1 is a spark plug.

このような第１実施形態においては、吸気弁用バルブシート６の外周側に設けられた壁部１０により、吸気弁２のバルブリフト量が極小リフト時の吸気行程では吸気流が壁部１０の壁面１０ａに衝突し、吸気流の筒内への流れが乱され、吸気弁小リフト時に比べて吸気流が筒内へ円滑に流れないようになっている。   In the first embodiment as described above, the wall portion 10 provided on the outer peripheral side of the valve seat 6 for the intake valve causes the intake flow to flow through the wall portion 10 during the intake stroke when the valve lift amount of the intake valve 2 is the minimum lift. Colliding with the wall surface 10a, the flow of the intake flow into the cylinder is disturbed, so that the intake flow does not flow smoothly into the cylinder compared to when the intake valve is small lifted.

そのため、吸気弁極小リフト時における吸入空気量が相対的に減少し、吸気弁開口面積の変化によって変わる吸入空気量の変化が小さくなって、吸気弁極小リフト時の吸入空気量のバラツキが低減されることになる。   Therefore, the amount of intake air at the time of minimum lift of the intake valve is relatively reduced, the change of the amount of intake air that changes due to the change of the opening area of the intake valve is reduced, and the variation in the amount of intake air at the time of minimum lift of the intake valve is reduced. Will be.

つまり、吸気弁小リフト時には吸気流動を低減させることなく、吸気弁極小リフト時においては吸気バルブリフト変化に対応する吸入空気量変化の割合を小さくすることができる。   That is, it is possible to reduce the intake air amount change ratio corresponding to the intake valve lift change during the intake valve minimum lift without reducing the intake flow during the intake valve small lift.

その結果、吸気弁極小リフト時にバルブリフト量の制御によってエンジン負荷を制御する場合に、吸気弁２のリフトばらつき幅の許容範囲を拡大することが可能になるため、可変動弁装置の製造時に要求される製造精度の基準緩和や、可変動弁装置の製造後に吸気弁のリフトばらつきを低減するために行う部品の選別行程の省略または簡素化をすることが可能になり、総じてコストを削減することが可能になる。   As a result, when the engine load is controlled by controlling the valve lift amount when the intake valve is minimally lifted, the allowable range of the lift variation width of the intake valve 2 can be expanded. It is possible to reduce the manufacturing accuracy standards and to omit or simplify the part selection process to reduce the lift variation of the intake valve after the manufacture of the variable valve operating system, thus reducing the overall cost. Is possible.

さらに、吸気弁２のバルブリフト量制御の精度を低下させても吸入空気量制御精度を保つことが可能になるため、バルブリフト量制御を簡易化することもできる。また、吸気弁小リフト時には吸気流が円滑に筒内に流れ込むため、吸気流動を強化することで燃焼を改善し燃費・未燃ＨＣ排出量を低減することが可能になる。   Furthermore, since the intake air amount control accuracy can be maintained even if the accuracy of the valve lift amount control of the intake valve 2 is lowered, the valve lift amount control can be simplified. In addition, since the intake flow smoothly flows into the cylinder during the small intake valve lift, it is possible to improve combustion and reduce fuel consumption and unburned HC emissions by enhancing the intake flow.

以下、本発明の他の実施形態について順次説明するが、上述した第１実施形態と共通する構成要素については、同一の符号を付し、重複する説明を省略する。   Hereinafter, other embodiments of the present invention will be sequentially described. However, the same reference numerals are given to components common to the above-described first embodiment, and redundant description will be omitted.

図４〜図６は、本発明の第２実施形態を示している。図４は、本発明の第２実施形態における内燃機関を模式的に示した説明図であって、ピストン側から見た内燃機関の燃焼室形状、換言すればシリンダヘッド側の燃焼室形状を示す説明図である。図５及び図６は、図４のＢ−Ｂ線に沿った断面図であり、図５は吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態を示し、図３は吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転を除く低負荷運転状態を示している。   4 to 6 show a second embodiment of the present invention. FIG. 4 is an explanatory view schematically showing the internal combustion engine in the second embodiment of the present invention, and shows the shape of the combustion chamber of the internal combustion engine viewed from the piston side, in other words, the shape of the combustion chamber on the cylinder head side. It is explanatory drawing. 5 and 6 are cross-sectional views taken along the line BB in FIG. 4. FIG. 5 shows the idle operation state after warm-up in which the valve lift amount of the intake valve 2 is a minimal lift, and FIG. The low load operation state excluding the idle operation after warm-up in which the valve lift amount of the valve 2 is a small lift is shown.

この第２実施形態は、図４に示すように、吸気弁用バルブシート６の中心から排気弁３方向に偏心した位置を中心として切削工具で上部壁面５に加工を行うことで、吸気弁２と排気弁３との間に結果的に第１壁部に相当する壁部１０が形成され、吸気弁用バルブシート６の相対的に反吸気導入方向側となる部分（吸気弁用バルブシート６の図４における左側略半分）の外周側に壁面１０ａが形成されたものである。   In the second embodiment, as shown in FIG. 4, the upper wall surface 5 is processed with a cutting tool around a position eccentric from the center of the valve seat 6 for the intake valve in the direction of the exhaust valve 3. As a result, a wall portion 10 corresponding to a first wall portion is formed between the intake valve valve seat 6 and the intake valve valve seat 6 which is on the side opposite to the intake air introduction direction (the intake valve valve seat 6 Wall surface 10a is formed on the outer peripheral side of the left half in FIG.

ここで、反吸気導入方向とは、具体的には、図４における左右方向の左側となる。これは、燃焼室４の中心に対して吸気ポート８が図４における左右方向の右側から燃焼室４に対して接続され、吸気ポート８の燃焼室４への開口部は、図４において右側の部分が相対的に吸気が導入される側に位置することになっているからである。そこで、燃焼室４の上部壁面５において、図４における左右方向の右側を吸気導入方向、図４における左右方向の左側を反吸気導入方向と定義する。   Here, the anti-intake air introduction direction is specifically the left side in the left-right direction in FIG. This is because the intake port 8 is connected to the combustion chamber 4 from the right in the left-right direction in FIG. 4 with respect to the center of the combustion chamber 4, and the opening of the intake port 8 to the combustion chamber 4 is on the right side in FIG. This is because the portion is relatively positioned on the side where the intake air is introduced. Therefore, in the upper wall surface 5 of the combustion chamber 4, the right side in the left-right direction in FIG. 4 is defined as the intake air introduction direction, and the left side in the left-right direction in FIG.

尚、第２実施形態における壁面１０ａの高さＭは、上述した第１実施形態と同様に設定されている。   In addition, the height M of the wall surface 10a in 2nd Embodiment is set similarly to 1st Embodiment mentioned above.

このような第２実施形態においても、吸気弁２のバルブリフト量が極小リフト時の吸気行程では吸気流が壁部１０の壁面１０ａに衝突し、吸気流の筒内への流れが乱され、吸気弁小リフト時に比べて吸気流が筒内へ円滑に流れないようになっている。   Also in the second embodiment, the intake flow collides with the wall surface 10a of the wall portion 10 in the intake stroke when the valve lift amount of the intake valve 2 is the minimum lift, and the flow of the intake flow into the cylinder is disturbed, The intake flow is prevented from flowing smoothly into the cylinder as compared with the case of small lift of the intake valve.

従って、この第２実施形態は、吸気弁用バルブシート６の反吸気導入方向側となる部分の外周側にのみ壁面１０ａを形成されている点で、吸気弁用バルブシート６の外周側の全周に亙って壁面１０ａが形成された第１実施形態よりも不利ではあるものの、上述した第１実施形態と同様の作用効果を得ることができる。   Therefore, in the second embodiment, the wall surface 10a is formed only on the outer peripheral side of the portion on the anti-intake introduction direction side of the intake valve valve seat 6, so that the entire outer peripheral side of the intake valve valve seat 6 is formed. Although it is more disadvantageous than the first embodiment in which the wall surface 10a is formed over the circumference, the same effect as the first embodiment described above can be obtained.

図７〜図９は、本発明の第３実施形態を示している。図７は、本発明の第３実施形態における内燃機関を模式的に示した説明図であって、ピストン側から見た内燃機関の燃焼室形状、換言すればシリンダヘッド側の燃焼室形状を示す説明図である。図８及び図９は、図７のＣ−Ｃ線に沿った断面図であり、図８は吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態を示し、図９は吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転を除く低負荷運転状態を示している。   7 to 9 show a third embodiment of the present invention. FIG. 7 is an explanatory view schematically showing the internal combustion engine in the third embodiment of the present invention, showing the shape of the combustion chamber of the internal combustion engine viewed from the piston side, in other words, the shape of the combustion chamber on the cylinder head side. It is explanatory drawing. 8 and 9 are cross-sectional views taken along the line CC of FIG. 7. FIG. 8 shows the idle operation state after warm-up in which the valve lift amount of the intake valve 2 is a minimum lift, and FIG. The low load operation state excluding the idle operation after warm-up in which the valve lift amount of the valve 2 is a small lift is shown.

この第３実施形態は、図７に示すように、吸気弁２と排気弁３との間の上部壁面に段差を設けることで、吸気弁２と排気弁３との間に結果的に第１壁部に相当する壁部１０が形成され、吸気弁２と排気弁３との間に壁面１０ａが形成されたものである。尚、第３実施形態における壁面１０ａの高さＭは、上述した第１実施形態と同様に設定されている。   As shown in FIG. 7, the third embodiment provides a step on the upper wall surface between the intake valve 2 and the exhaust valve 3, resulting in a first difference between the intake valve 2 and the exhaust valve 3. A wall portion 10 corresponding to the wall portion is formed, and a wall surface 10 a is formed between the intake valve 2 and the exhaust valve 3. Note that the height M of the wall surface 10a in the third embodiment is set in the same manner as in the first embodiment described above.

このような第３実施形態においても、吸気弁２のバルブリフト量が極小リフト時の吸気行程では吸気流が壁部１０の壁面１０ａに衝突し、吸気流の筒内への流れが乱され、吸気弁小リフト時に比べて吸気流が筒内へ円滑に流れないようになっている。   Also in the third embodiment, the intake flow collides with the wall surface 10a of the wall portion 10 in the intake stroke when the valve lift amount of the intake valve 2 is the minimum lift, and the flow of the intake flow into the cylinder is disturbed. The intake flow is prevented from flowing smoothly into the cylinder as compared with the case of small lift of the intake valve.

従って、このような第３実施形態においては、吸気弁用バルブシート６の外周側の全周に亙って壁面１０ａが形成されていない点で上述した第１実施形態よりも不利であるものの、上述した第１実施形態と同様の作用効果を得ることができる。   Therefore, in such a third embodiment, although it is disadvantageous compared to the first embodiment described above in that the wall surface 10a is not formed over the entire outer periphery of the intake valve valve seat 6, The same effect as the first embodiment described above can be obtained.

図１０〜図１２は、本発明の第４実施形態を示している。図１０は、本発明の第４実施形態における内燃機関を模式的に示した説明図であって、ピストン側から見た内燃機関の燃焼室形状、換言すればシリンダヘッド側の燃焼室形状を示す説明図である。図１１及び図１２は、図１０のＤ−Ｄ線に沿った断面図であり、図１１は吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態を示し、図１２は吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転を除く低負荷運転状態を示している。   10 to 12 show a fourth embodiment of the present invention. FIG. 10 is an explanatory view schematically showing the internal combustion engine in the fourth embodiment of the present invention, showing the shape of the combustion chamber of the internal combustion engine viewed from the piston side, in other words, the shape of the combustion chamber on the cylinder head side. It is explanatory drawing. 11 and 12 are cross-sectional views taken along the line D-D in FIG. 10. FIG. 11 shows the idle operation state after warm-up in which the valve lift amount of the intake valve 2 is a minimum lift, and FIG. The low load operation state excluding the idle operation after warm-up in which the valve lift amount of the valve 2 is a small lift is shown.

この第４実施形態においては、図１１及び図１２に示すように、吸気弁用バルブシート６を燃焼室４の上部壁面５よりも吸気上流側に後退させることで、結果的に第１壁部に相当する壁部１０が形成され、この壁部１０の壁面１０ａによって吸気弁用バルブシート６の外周側を全周に亙って囲まれている。尚、第４実施形態における壁面１０ａの高さＭは、上述した第１実施形態と同様に設定されている。   In the fourth embodiment, as shown in FIGS. 11 and 12, the intake valve valve seat 6 is retracted to the intake upstream side of the upper wall surface 5 of the combustion chamber 4, resulting in the first wall portion. Is formed, and the outer peripheral side of the intake valve valve seat 6 is surrounded by the wall surface 10a of the wall 10 over the entire circumference. In addition, the height M of the wall surface 10a in 4th Embodiment is set similarly to 1st Embodiment mentioned above.

このような第４実施形態においても、吸気弁２のバルブリフト量が極小リフト時の吸気行程では吸気流が壁部１０の壁面１０ａに衝突し、吸気流の筒内への流れが乱され、吸気弁小リフト時に比べて吸気流が筒内へ円滑に流れないようになっている。   Also in the fourth embodiment, the intake flow collides with the wall surface 10a of the wall portion 10 in the intake stroke when the valve lift amount of the intake valve 2 is the minimum lift, and the flow of the intake flow into the cylinder is disturbed, The intake flow is prevented from flowing smoothly into the cylinder as compared with the case of small lift of the intake valve.

従って、この第４実施形態においては、上述した第１実施形態と略同様の作用効果を得ることができる。   Therefore, in the fourth embodiment, it is possible to obtain substantially the same operational effects as those of the first embodiment described above.

図１３〜図１５は、本発明の第５実施形態を示している。図１３は、本発明の第５実施形態における内燃機関を模式的に示した説明図であって、ピストン側から見た内燃機関の燃焼室形状、換言すればシリンダヘッド側の燃焼室形状を示す説明図である。図１４及び図１５は、図１３のＥ−Ｅ線に沿った断面図であり、図１４は吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態を示し、図１５は吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転を除く低負荷運転状態を示している。   13 to 15 show a fifth embodiment of the present invention. FIG. 13 is an explanatory view schematically showing the internal combustion engine in the fifth embodiment of the present invention, and shows the shape of the combustion chamber of the internal combustion engine viewed from the piston side, in other words, the shape of the combustion chamber on the cylinder head side. It is explanatory drawing. 14 and 15 are cross-sectional views taken along the line E-E in FIG. 13. FIG. 14 shows the idle operation state after warm-up in which the valve lift amount of the intake valve 2 is a minimum lift, and FIG. The low load operation state excluding the idle operation after warm-up in which the valve lift amount of the valve 2 is a small lift is shown.

この第５実施形態は、上述した第２実施形態において、吸気弁用バルブシート６の相対的に吸気導入方向側となる部分（吸気弁用バルブシート６の図１３における右側半分）の外周側に、吸気弁リフト方向に沿って突出する第２壁部２１が形成されたものである。   This fifth embodiment is the same as the second embodiment described above on the outer peripheral side of the portion of the intake valve valve seat 6 that is relatively on the intake introduction direction side (the right half in FIG. 13 of the intake valve seat 6). A second wall portion 21 that protrudes along the intake valve lift direction is formed.

また、吸気弁２のバルブヘッド１１の側面１１ａと対向する第２壁部２１の壁面２１ａの高さＮ、すなわち第２壁部２１のバルブリフト方向への突き出し量Ｎは、吸気弁２着座位置を基準として、暖機後アイドルを除く低負荷運転状態時の最大リフト量（小リフト量Ｒｍａｘ）よりも僅かに大きくなるよう設定されている。   The height N of the wall surface 21a of the second wall 21 facing the side surface 11a of the valve head 11 of the intake valve 2, that is, the protrusion amount N of the second wall 21 in the valve lift direction is the intake valve 2 seating position. Is set to be slightly larger than the maximum lift amount (small lift amount Rmax) in a low-load operation state excluding idle after warm-up.

尚、第５実施形態における壁面１０ａの高さＭは、上述した第１実施形態と同様に設定されている。   In addition, the height M of the wall surface 10a in 5th Embodiment is set similarly to 1st Embodiment mentioned above.

このような第５実施形態においては、吸気弁用バルブシート６の吸気導入方向側の外周側に第２壁部２１を設けることによって、吸気弁２のバルブリフト量が極小リフトまたは小リフト時において、吸気弁開口面積を減少させかつ高速の指向性のある吸気流動を生じさせることができる。   In the fifth embodiment, by providing the second wall portion 21 on the outer peripheral side of the intake valve valve seat 6 on the intake introduction direction side, when the valve lift amount of the intake valve 2 is minimal lift or small lift, The intake valve opening area can be reduced and high-speed directional intake flow can be generated.

そのため、上述した第１形態と同様の作用効果に加え、第２壁部２１による吸気流動の強化により、吸気弁２のバルブリフト量が極小リフトまたは小リフト時における燃焼を改善することが可能になる。   Therefore, in addition to the same effects as the first embodiment described above, the intake flow is enhanced by the second wall portion 21, so that it is possible to improve the combustion when the valve lift amount of the intake valve 2 is the minimum lift or the small lift. Become.

図１６〜図１８は、本発明の第６実施形態を示している。図１６は、本発明の第６実施形態における内燃機関を模式的に示した説明図であって、ピストン側から見た内燃機関の燃焼室形状、換言すればシリンダヘッド側の燃焼室形状を示す説明図である。図１７及び図１８は、図１６のＦ−Ｆ線に沿った断面図であり、図１７は吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態を示し、図１８は吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転を除く低負荷運転状態を示している。   16 to 18 show a sixth embodiment of the present invention. FIG. 16 is an explanatory view schematically showing the internal combustion engine in the sixth embodiment of the present invention, showing the shape of the combustion chamber of the internal combustion engine viewed from the piston side, in other words, the shape of the combustion chamber on the cylinder head side. It is explanatory drawing. 17 and 18 are cross-sectional views taken along the line FF in FIG. 16. FIG. 17 shows the idle operation state after warm-up in which the valve lift amount of the intake valve 2 is a minimum lift, and FIG. The low load operation state excluding the idle operation after warm-up in which the valve lift amount of the valve 2 is a small lift is shown.

この第６実施形態においては、排気弁３閉時、すなわち排気弁３の排気弁用バルブシート６に着座した状態時における排気弁３の上部壁面５からの突き出し量Ｓが、吸気弁２のバルブリフト量が極小リフトとなる暖機後アイドル運転状態時における吸気弁２の最大リフト量Ｐｍａｘよりも大きく、かつ吸気弁２のバルブリフト量が小リフトとなる暖機後アイドル運転状態を除く低負荷運転状態時における吸気弁２最大リフト量Ｒｍａｘよりも小さくなるように設定されている。   In the sixth embodiment, when the exhaust valve 3 is closed, that is, when the exhaust valve 3 is seated on the exhaust valve valve seat 6, the protrusion amount S from the upper wall surface 5 of the exhaust valve 3 is the valve of the intake valve 2. Low load excluding the warm-up idle operation state in which the lift amount is larger than the maximum lift amount Pmax of the intake valve 2 during the warm-up idle operation state where the lift amount is a minimal lift and the valve lift amount of the intake valve 2 is a small lift The intake valve 2 is set to be smaller than the maximum lift amount Rmax in the operating state.

つまり、この第６実施形態においては、排気弁３の着座時に上部壁面５からの突き出した排気弁３のバルブヘッド１４が、第１壁部に相当する構成となっている。   That is, in the sixth embodiment, the valve head 14 of the exhaust valve 3 protruding from the upper wall surface 5 when the exhaust valve 3 is seated corresponds to the first wall portion.

このような第６実施形態においては、吸気弁２のバルブリフト量が極小リフト時の吸気行程では吸気流が上部壁面５から突き出した排気弁３のバルブヘッド１４の側面１４ａに衝突し、吸気流の筒内への流れが乱され、吸気弁小リフト時に比べて吸気流が筒内へ円滑に流れないようになっている。   In such a sixth embodiment, the intake flow collides with the side surface 14a of the valve head 14 of the exhaust valve 3 protruding from the upper wall surface 5 during the intake stroke when the valve lift amount of the intake valve 2 is the minimum lift, and the intake flow As a result, the flow of air into the cylinder is disturbed, so that the intake flow does not flow smoothly into the cylinder as compared to when the intake valve is small lifted.

従って、このような第６実施形態においては、上述した第１実施形態よりも不利であるものの、上述した第１実施形態と同様の作用効果を得ることができる。   Therefore, in such a sixth embodiment, although it is more disadvantageous than the first embodiment described above, it is possible to obtain the same effects as the first embodiment described above.

上記各実施形態から把握し得る本発明の技術的思想について、その効果とともに列記する。   The technical ideas of the present invention that can be grasped from the above embodiments will be listed together with the effects thereof.

（１） 機関負荷に応じて吸気弁のバルブリフト量を変更可能な内燃機関において、吸気弁のバルブリフト量が小リフト時の吸気行程では吸気流が筒内に円滑に流れ込むが、吸気弁のバルブリフト量が極小リフト時の吸気行程では吸気流の筒内への流れが乱されるよう構成されている。   (1) In an internal combustion engine in which the valve lift amount of the intake valve can be changed according to the engine load, the intake flow smoothly flows into the cylinder during the intake stroke when the valve lift amount of the intake valve is small. In the intake stroke when the valve lift amount is a minimum lift, the flow of the intake flow into the cylinder is disturbed.

これによって、吸気弁極小リフト時における吸入空気量が相対的に減少し、吸気弁開口面積の変化によって変わる吸入空気量の変化が小さくなって、吸気弁極小リフト時の吸入空気量のバラツキが低減されることになる。そのため、吸気弁の極小リフト時のリフトばらつき幅の許容範囲を拡大可能となり、製造後に吸気弁のリフトばらつきを低減するために行う必要があった部品の選別行程を、省略または簡素化することが可能になるため、コストを削減することが可能になる。   As a result, the intake air amount at the time of the intake valve minimum lift is relatively reduced, the change in the intake air amount that changes due to the change in the intake valve opening area is reduced, and the variation in the intake air amount at the time of the intake valve minimum lift is reduced. Will be. Therefore, it is possible to expand the allowable range of the lift variation width at the time of the minimum lift of the intake valve, and it is possible to omit or simplify the part selection process that was necessary to reduce the lift variation of the intake valve after manufacturing. This makes it possible to reduce costs.

（２） 上記（１）に記載の内燃機関は、具体的には、燃焼室壁面形状によって吸気弁のバルブリフト量が極小リフト時の吸気行程での吸気流の筒内への流れが乱される。   (2) In the internal combustion engine described in (1) above, specifically, the flow of the intake air into the cylinder during the intake stroke when the valve lift amount of the intake valve is the minimum lift is disturbed by the shape of the wall surface of the combustion chamber. The

（３） 上記（１）または（２）に記載の内燃機関は、具体的には、吸気弁のバルブシート近傍の燃焼室壁面に形成された第１壁部によって、吸気弁のバルブリフト量が極小リフト時の吸気行程での吸気流の筒内への流れが乱される。   (3) In the internal combustion engine described in the above (1) or (2), specifically, the valve lift amount of the intake valve is increased by the first wall portion formed on the wall surface of the combustion chamber near the valve seat of the intake valve. The flow of the intake flow into the cylinder during the intake stroke during the minimum lift is disturbed.

（４） 上記（３）に記載の内燃機関は、より具体的には、第１壁部が、吸気弁のバルブリフト量が極小リフトとなる運転状態時の吸気弁最大リフト量よりも高く、かつ吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも低くなるように形成されている。   (4) In the internal combustion engine according to (3), more specifically, the first wall portion is higher than the intake valve maximum lift amount in an operation state in which the valve lift amount of the intake valve is a minimum lift, And it is formed so that the valve lift amount of the intake valve is lower than the maximum lift amount of the intake valve in the operation state where the lift is small.

（５） 上記（１）〜（４）のいずれかに記載の内燃機関において、吸気弁のバルブリフト量が小リフトまたは極小リフトとなる運転状態時に、吸気弁開口面積を減少させかつ高速の指向性のある吸気流動を生じるよう吸気弁のバルブシートの外周側に第２壁部が形成されている。これによって、吸気弁のバルブリフト量が極小リフトまたは小リフト時における燃焼を改善することが可能になる。   (5) In the internal combustion engine according to any one of (1) to (4), when the valve lift amount of the intake valve is a small lift or a minimal lift, the intake valve opening area is reduced and high speed directing is performed. A second wall portion is formed on the outer peripheral side of the valve seat of the intake valve so as to generate a characteristic intake flow. This makes it possible to improve the combustion when the valve lift amount of the intake valve is a minimum lift or a small lift.

（６） 上記（１）〜（５）のいずれかに記載の内燃機関において、排気弁閉時における排気弁のバルブヘッドの燃焼室壁面からの突き出し量が、吸気弁のバルブリフト量が極小リフトとなる運転状態時の吸気弁最大リフト量よりも大きく、かつ吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも小さくなるように設定されている。   (6) In the internal combustion engine according to any one of (1) to (5), the amount of protrusion of the exhaust valve from the combustion chamber wall surface of the valve head when the exhaust valve is closed is the minimum lift of the intake valve. It is set to be larger than the maximum lift amount of the intake valve in the operating state, and smaller than the maximum lift amount of the intake valve in the operating state where the valve lift amount of the intake valve is a small lift.

本発明の第１実施形態における内燃機関を模式的に示した説明図。BRIEF DESCRIPTION OF THE DRAWINGS Explanatory drawing which showed typically the internal combustion engine in 1st Embodiment of this invention. 暖機後アイドル運転状態時における図１のＡ−Ａ線に沿った断面図。Sectional drawing in alignment with the AA of FIG. 1 at the time of an idle driving | running state after warming-up. 暖機後アイドル運転を除く低負荷運転状態時における図１のＡ−Ａ線に沿った断面図。Sectional drawing in alignment with the AA of FIG. 1 at the time of the low load driving | running state except idle operation after warming-up. 本発明の第２実施形態における内燃機関を模式的に示した説明図。Explanatory drawing which showed typically the internal combustion engine in 2nd Embodiment of this invention. 暖機後アイドル運転状態時における図４のＢ−Ｂ線に沿った断面図。Sectional drawing in alignment with the BB line of FIG. 4 at the time of idle operation state after warming-up. 暖機後アイドル運転を除く低負荷運転状態時における図４のＢ−Ｂ線に沿った断面図。Sectional drawing along the BB line | wire of FIG. 4 at the time of the low load driving | running state except idle operation after warming-up. 本発明の第３実施形態における内燃機関を模式的に示した説明図。Explanatory drawing which showed typically the internal combustion engine in 3rd Embodiment of this invention. 暖機後アイドル運転状態時における図７のＣ−Ｃ線に沿った断面図。Sectional drawing along CC line of FIG. 7 at the time of idle operation state after warming-up. 暖機後アイドル運転を除く低負荷運転状態時における図７のＣ−Ｃ線に沿った断面図。Sectional drawing along CC line of FIG. 7 at the time of the low load driving | running state except idle operation after warming-up. 本発明の第４実施形態における内燃機関を模式的に示した説明図。Explanatory drawing which showed typically the internal combustion engine in 4th Embodiment of this invention. 暖機後アイドル運転状態時における図１０のＤ−Ｄ線に沿った断面図。Sectional drawing in alignment with the DD line | wire of FIG. 10 at the time of idle operation state after warming-up. 暖機後アイドル運転を除く低負荷運転状態時における図１０のＤ−Ｄ線に沿った断面図。Sectional drawing along the DD line | wire of FIG. 10 at the time of the low load driving | running state except idle operation after warming-up. 本発明の第５実施形態における内燃機関を模式的に示した説明図。Explanatory drawing which showed typically the internal combustion engine in 5th Embodiment of this invention. 暖機後アイドル運転状態時における図１３のＥ−Ｅ線に沿った断面図。Sectional drawing along the EE line | wire of FIG. 13 at the time of idle operation state after warming-up. 暖機後アイドル運転を除く低負荷運転状態時における図１３のＥ−Ｅ線に沿った断面図。Sectional drawing along the EE line | wire of FIG. 13 at the time of the low load driving | running state except idle operation after warming-up. 本発明の第６実施形態における内燃機関を模式的に示した説明図。Explanatory drawing which showed typically the internal combustion engine in 6th Embodiment of this invention. 暖機後アイドル運転状態時における図１６のＦ−Ｆ線に沿った断面図。Sectional drawing in alignment with the FF line | wire of FIG. 16 at the time of an idle driving | running state after warming up. 暖機後アイドル運転を除く低負荷運転状態時における図１６のＦ−Ｆ線に沿った断面図。Sectional drawing along the FF line | wire of FIG. 16 at the time of the low load driving | running state except idle operation after warming-up.

符号の説明Explanation of symbols

２…吸気弁
５…上部壁面
６…吸気弁用バルブシート
１０…壁部
２１…第２壁部 2 ... Intake valve 5 ... Upper wall surface 6 ... Valve seat for intake valve 10 ... Wall portion 21 ... Second wall portion

Claims (5)

機関負荷に応じて吸気弁のバルブリフト量を変更可能な内燃機関において、
吸気弁のバルブシートの外周側の燃焼室壁面には、吸気弁のバルブリフト量が極小リフトとなる運転状態時における吸入空気量が相対的に減少するよう、吸気弁のバルブリフト量が極小リフトとなる運転状態時の吸気弁最大リフト量よりも高く、かつ吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも低くなる第１壁部が、吸気弁のバルブシートの外周を全周に亙って囲むように形成されていることを特徴とする内燃機関。 In an internal combustion engine that can change the valve lift amount of the intake valve according to the engine load,
The intake valve valve lift amount is minimally lifted on the combustion chamber wall on the outer periphery of the valve seat of the intake valve so that the intake air amount is relatively reduced during the operation state in which the valve lift amount of the intake valve is minimal lift. The first wall portion, which is higher than the intake valve maximum lift amount in the operating state and becomes lower than the intake valve maximum lift amount in the operating state where the intake valve valve lift amount is a small lift, is the valve of the intake valve An internal combustion engine characterized in that the outer periphery of the seat is formed so as to surround the entire periphery . 機関負荷に応じて吸気弁のバルブリフト量を変更可能な内燃機関において、In an internal combustion engine that can change the valve lift amount of the intake valve according to the engine load,
燃焼室において吸気ポートが接続されている側を吸気導入方向側とし、燃焼室において排気ポートが接続されている側を反吸気導入方向側とした場合、  When the side where the intake port is connected in the combustion chamber is the intake introduction direction side, and the side where the exhaust port is connected in the combustion chamber is the anti-intake introduction direction side,
吸気弁のバルブシートの外周側の燃焼室壁面には、吸気弁のバルブリフト量が極小リフトとなる運転状態時における吸入空気量が相対的に減少するよう、吸気弁のバルブリフト量が極小リフトとなる運転状態時の吸気弁最大リフト量よりも高く、かつ吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも低くなる第１壁部が、吸気弁のバルブシートの外周の反吸気導入方向側の部分を囲むように形成されていることを特徴とする内燃機関。  The intake valve valve lift amount is minimally lifted on the combustion chamber wall on the outer periphery of the valve seat of the intake valve so that the intake air amount is relatively reduced during the operation state in which the valve lift amount of the intake valve is minimal lift. The first wall portion, which is higher than the intake valve maximum lift amount in the operating state and becomes lower than the intake valve maximum lift amount in the operating state where the intake valve valve lift amount is a small lift, is the valve of the intake valve An internal combustion engine characterized by being formed so as to surround a portion of the outer periphery of the seat on the side opposite to the intake direction. 機関負荷に応じて吸気弁のバルブリフト量を変更可能な内燃機関において、In an internal combustion engine that can change the valve lift amount of the intake valve according to the engine load,
燃焼室の上部壁面には、吸気弁と排気弁との間を通る直線状の段差が形成され、当該段差の吸気弁バルブリフト方向の高さは、吸気弁のバルブリフト量が極小リフトとなる運転状態時における吸入空気量が相対的に減少するよう、吸気弁のバルブリフト量が極小リフトとなる運転状態時の吸気弁最大リフト量よりも高く、かつ吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも低くなるよう形成されていることを特徴とする内燃機関。  On the upper wall surface of the combustion chamber, a linear step is formed passing between the intake valve and the exhaust valve. The height of the step in the intake valve lift direction is such that the valve lift amount of the intake valve is a minimum lift. In order to relatively reduce the intake air amount during the operation state, the valve lift amount of the intake valve is higher than the intake valve maximum lift amount during the operation state where the lift valve is a minimum lift, and the valve lift amount of the intake valve is a small lift. An internal combustion engine configured to be lower than a maximum lift amount of the intake valve in an operating state. 吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも高くなる第２壁部が、吸気弁のバルブシートの外周の吸気導入方向側となる部分を囲むように形成されていることを特徴とする請求項２に記載の内燃機関。  The second wall part, which is higher than the intake valve maximum lift amount in the operating state where the valve lift amount of the intake valve is a small lift, is formed so as to surround the portion on the intake valve introduction side on the outer periphery of the valve seat of the intake valve The internal combustion engine according to claim 2, wherein the internal combustion engine is provided. ペントルーフ型の燃焼室を有し、機関負荷に応じて吸気弁のバルブリフト量を変更可能な内燃機関において、In an internal combustion engine that has a pent roof type combustion chamber and can change the valve lift amount of the intake valve according to the engine load,
排気弁閉時における排気弁のバルブヘッドの燃焼室壁面からの突き出し量が、吸気弁のバルブリフト量が極小リフトとなる運転状態時の吸気弁最大リフト量よりも大きく、かつ吸気弁のバルブリフト量が小リフトとなる運転状態時の吸気弁最大リフト量よりも小さくなるように設定されていることを特徴とする内燃機関。  When the exhaust valve is closed, the amount of protrusion of the valve head of the exhaust valve from the combustion chamber wall surface is larger than the maximum lift amount of the intake valve in the operating state where the valve lift amount of the intake valve is a minimum lift, and the valve lift of the intake valve An internal combustion engine characterized by being set to be smaller than an intake valve maximum lift amount in an operating state in which the amount is a small lift.
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JP4712844B2 (en) * 2008-08-01 2011-06-29 本田技研工業株式会社 Combustion chamber structure of internal combustion engine
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Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5657906U (en) * 1979-10-09 1981-05-19
JPH0578953U (en) * 1992-03-30 1993-10-26 三菱自動車工業株式会社 Internal combustion engine combustion chamber structure
JPH09112284A (en) * 1995-09-21 1997-04-28 Meta Motoren & Energ Technik Gmbh Reciprocation-piston internal combusion engine
JPH10504367A (en) * 1994-08-11 1998-04-28 デル・ウエスト・エンジニアリング・インコーポレーテッド Titanium engine valve
JP2003314230A (en) * 2002-04-22 2003-11-06 Nissan Motor Co Ltd Combustion chamber structure of engine

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5657906U (en) * 1979-10-09 1981-05-19
JPH0578953U (en) * 1992-03-30 1993-10-26 三菱自動車工業株式会社 Internal combustion engine combustion chamber structure
JPH10504367A (en) * 1994-08-11 1998-04-28 デル・ウエスト・エンジニアリング・インコーポレーテッド Titanium engine valve
JPH09112284A (en) * 1995-09-21 1997-04-28 Meta Motoren & Energ Technik Gmbh Reciprocation-piston internal combusion engine
JP2003314230A (en) * 2002-04-22 2003-11-06 Nissan Motor Co Ltd Combustion chamber structure of engine

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