JP2000027612A - Seat ring for intake valve and gas engine - Google Patents

Seat ring for intake valve and gas engine

Info

Publication number
JP2000027612A
JP2000027612A JP10195896A JP19589698A JP2000027612A JP 2000027612 A JP2000027612 A JP 2000027612A JP 10195896 A JP10195896 A JP 10195896A JP 19589698 A JP19589698 A JP 19589698A JP 2000027612 A JP2000027612 A JP 2000027612A
Authority
JP
Japan
Prior art keywords
seat ring
center
intake
inner diameter
eccentric
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP10195896A
Other languages
Japanese (ja)
Other versions
JP3715437B2 (en
Inventor
Satoru Goto
悟 後藤
Eibun Nishi
栄文 西
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Niigata Engineering Co Ltd
Original Assignee
Niigata Engineering Co Ltd
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Niigata Engineering Co Ltd filed Critical Niigata Engineering Co Ltd
Priority to JP19589698A priority Critical patent/JP3715437B2/en
Publication of JP2000027612A publication Critical patent/JP2000027612A/en
Application granted granted Critical
Publication of JP3715437B2 publication Critical patent/JP3715437B2/en
Anticipated expiration legal-status Critical
Expired - Lifetime legal-status Critical Current

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Classifications

    • 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
    • Y02T10/30—Use of alternative fuels, e.g. biofuels

Landscapes

  • Cylinder Crankcases Of Internal Combustion Engines (AREA)
  • Combustion Methods Of Internal-Combustion Engines (AREA)

Abstract

PROBLEM TO BE SOLVED: To provide a seat ring for intake valve capable of setting a sufficient value of swirl ratio and coefficient of flow at the same time. SOLUTION: A seat ring 1 is not formed into the concentric circle, and the center of the outer diameter and the center of the inner diameter of a hole part 2 diviate from each other. The inner peripheral surface of the hole part 2 is formed of a peripheral surface at an inner diameter ϕB having the center (b) displaced from the center (a) of the outer diameter by E. Direction from the center (a) of the outer diameter to the center (b) of the inner diameter is named eccentric direction. The peripheral surface having the center (a) and the inner diameter ϕA is firstly formed, and thereafter, the peripheral surface having the center (b) and the inner diameter ϕB is worked. A rear peripheral surface in the eccentric direction is formed into a projecting peripheral surface 2a as a peripheral surface having the inner diameter ϕA, and a front part in the eccentric direction is formed into a flat peripheral surface 2b. The seat ring 1 is fitted so that the eccentric direction thereof is nearly opposite to the intake direction of the air supplied from an intake port to a combustion chamber. With this structure, sufficient values of swirl ratio and coefficient of flow can be obtained at the same time.

Description

【発明の詳細な説明】DETAILED DESCRIPTION OF THE INVENTION

【０００１】[0001]

【発明の属する技術分野】本考案は、希薄燃焼ガスエン
ジンの燃焼性を改善して、低ＮＯｘを維持しながら、よ
り高いエンジン熱効率を達成しうる吸気弁のシートリン
グに関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a seat ring of an intake valve which can improve the flammability of a lean burn gas engine and achieve higher engine thermal efficiency while maintaining low NOx.

【０００２】[0002]

【従来の技術】ガスエンジン等の内燃機関においては、
燃焼室に連通する吸気ポートの開口にはシートリングが
取り付けられており、この開口を開閉する吸気弁が当接
するためのシート面を提供するようになっている。従来
のシートリング形状は、図９に示す様に同芯円加工によ
る単純な形状であった。当然、中心の孔部の内径の中心
と、外径の中心は、中心軸Ｃにおいて一致している。2. Description of the Related Art In an internal combustion engine such as a gas engine,
A seat ring is attached to an opening of an intake port that communicates with the combustion chamber, and provides a seat surface with which an intake valve that opens and closes the opening abuts. The conventional seat ring shape was a simple shape formed by concentric processing as shown in FIG. Naturally, the center of the inner diameter of the center hole and the center of the outer diameter coincide with each other on the center axis C.

【０００３】[0003]

【発明が解決しようとする課題】従来のシートリング形
状は、前述したように単純な同心円形状であった。この
ため、このタイプのシートリングを組み込んだガスエン
ジンではスワール比が小さく、空気流動を利用して燃焼
性を改善する効果を得ることができなかった。燃料ガス
と空気の混合気の燃焼が火炎伝播によって行われること
を考慮すると、空気流動の積極的利用が短期燃焼を実現
し、熱効率の向上に寄与すると本願発明者は考えた。即
ち、従来のガスエンジンにおけるシートリングでは、上
記観点からみて技術開発の余地が残されていた。The conventional seat ring shape is a simple concentric circle shape as described above. For this reason, in a gas engine incorporating this type of seat ring, the swirl ratio is small, and it has not been possible to obtain the effect of improving the combustibility by utilizing the air flow. In view of the fact that the combustion of the mixture of fuel gas and air is performed by flame propagation, the inventor of the present application considered that active use of the air flow would realize short-term combustion and contribute to improvement in thermal efficiency. That is, the seat ring of the conventional gas engine leaves room for technical development from the above viewpoint.

【０００４】しかしながら、スワール流の強化は吸気弁
の流量係数を低下させる事となり、高負荷域での空気不
足を招く。このため、スワール流の強化には、排気温度
上昇やノッキングなどの問題も内在していた。[0004] However, the strengthening of the swirl flow decreases the flow coefficient of the intake valve, resulting in a shortage of air in a high load region. For this reason, problems such as an increase in exhaust gas temperature and knocking were inherent in the enhancement of swirl flow.

【０００５】本発明は、従来相反する項目と考えられて
いたスワール比と流量係数について同時に十分な値を設
定することができる吸気弁のシートリングを提供するこ
とを目的としている。An object of the present invention is to provide a seat ring of an intake valve that can simultaneously set a sufficient value for a swirl ratio and a flow coefficient, which have been considered as contradictory items.

【０００６】[0006]

【課題を解決するための手段】請求項１に記載された給
気弁のシートリング（１）は、内燃機関の燃焼室に連通
する吸気ポート（１０）の開口に取り付けられ、前記給
気ポートの開口を開閉する吸気弁が当接するシートリン
グにおいて、中央に開口した孔部（２）の内径の中心
（ｂ）が、外径の中心（ａ）に対して偏芯していること
を特徴としている。According to a first aspect of the present invention, a seat ring (1) for an air supply valve is attached to an opening of an intake port (10) communicating with a combustion chamber of an internal combustion engine, and the air supply port is provided with the seat ring. The center (b) of the inner diameter of the hole (2) opened in the center is eccentric with respect to the center (a) of the outer diameter in the seat ring contacting the intake valve that opens and closes the opening. And

【０００７】請求項２に記載された吸気弁のシートリン
グは、請求項１記載の吸気弁のシートリング（１）にお
いて、前記外径の中心（ａ）から前記内径の中心（ｂ）
に向かう前記シートリングの偏芯方向が、前記吸気ポー
ト（１０）から前記燃焼室に供給される吸気の方向に対
して略反対向きとなるように、前記シートリングを前記
開口に取り付けたことを特徴としている。According to a second aspect of the present invention, there is provided an intake valve seat ring according to the first aspect, wherein the center of the outer diameter is located at the center of the inner diameter of the seat ring of the intake valve.
The seat ring is attached to the opening such that an eccentric direction of the seat ring toward the intake port is substantially opposite to a direction of intake air supplied from the intake port (10) to the combustion chamber. Features.

【０００８】請求項３に記載された吸気弁のシートリン
グは、請求項１記載の吸気弁のシートリング（１）にお
いて、前記シートリングの前記孔部（２）の内周面の
内、前記シートリングの偏芯方向について前方の部分
（２ｂ）が、前記開口部の中心軸と平行な平面における
断面で直線状を呈し、かつ前記シートリングの偏芯方向
について後方の部分（２ａ）が、前記開口部の中心軸と
平行な平面における断面で円周状を呈するように構成し
たことを特徴としている。According to a third aspect of the present invention, there is provided the seat ring of the intake valve according to the first aspect, wherein the seat ring of the intake valve according to the first aspect includes an inner peripheral surface of the hole (2) of the seat ring. A portion (2b) in front of the eccentric direction of the seat ring has a linear shape in a cross section in a plane parallel to the central axis of the opening, and a portion (2a) behind in the eccentric direction of the seat ring is It is characterized in that the opening is formed to have a circumferential shape in a cross section in a plane parallel to a central axis of the opening.

【０００９】請求項４に記載された吸気弁のシートリン
グ（１）は、内燃機関の燃焼室に連通する吸気ポート
（１０）の２つの開口に取り付けられ、前記各開口を開
閉する２つの吸気弁がそれぞれ当接する２つのシートリ
ングにおいて、各シートリングともに中央に開口した孔
部（２）の内径の中心（ｂ）が外径の中心（ａ）に対し
て偏芯しており、前記外径の中心から前記内径の中心に
向かう方向を前記シートリングの偏芯方向とし、かつ前
記吸気ポートから吸入される吸気の流れの方向を１２時
とした場合、前記流れに沿って上流側のシートリングの
偏芯方向が６時から９時の角度範囲に設定され、前記流
れに沿って下流側のシートリングの偏芯方向が３時から
６時の角度範囲に設定されたことを特徴としている。A seat ring (1) for an intake valve according to a fourth aspect is attached to two openings of an intake port (10) communicating with a combustion chamber of an internal combustion engine, and two intakes for opening and closing the respective openings. In the two seat rings with which the valves abut, respectively, the center (b) of the inner diameter of the hole (2) opened at the center of each of the seat rings is eccentric with respect to the center (a) of the outer diameter. When the direction from the center of the diameter toward the center of the inner diameter is the eccentric direction of the seat ring, and the direction of the flow of the intake air sucked from the intake port is 12:00, the upstream seat along the flow is provided. The eccentric direction of the ring is set in the angle range from 6:00 to 9:00, and the eccentric direction of the downstream seat ring along the flow is set in the angle range from 3:00 to 6:00. .

【００１０】請求項５に記載されたガスエンジンは、請
求項１又は２又は３又は４に記載した吸気弁のシートリ
ング（１）を備えたことにより、スワール比と流量係数
について同時に十分な値を達成することを特徴としてい
る。A gas engine according to a fifth aspect of the present invention includes the seat ring (1) of the intake valve according to the first, second, third, or fourth aspect of the present invention. Is achieved.

【００１１】[0011]

【発明の実施の形態】本発明は、ガスエンジンのシリン
ダヘッドに装着される吸気弁シートリングの形状を改良
し、流量係数の低下を見ることなく、スワール流の強化
によって空気流動を促進して燃焼性を改善する効果を得
るものである。本考案は、火炎伝播による燃焼形態を採
るエンジン、つまりパイロット燃料油着火ガスエンジ
ン、火花点火ガスエンジン、火花点火ガソリンエンジン
等に適用できる。また、本発明の技術を採用したエンジ
ンは、例えば産業用と民生用の定置型発電設備として利
用される。DESCRIPTION OF THE PREFERRED EMBODIMENTS The present invention improves the shape of an intake valve seat ring mounted on a cylinder head of a gas engine, and promotes air flow by enhancing swirl flow without observing a decrease in flow coefficient. The effect of improving the flammability is obtained. INDUSTRIAL APPLICABILITY The present invention can be applied to an engine that adopts a combustion mode by flame propagation, that is, a pilot fuel oil ignition gas engine, a spark ignition gas engine, a spark ignition gasoline engine, and the like. Further, the engine employing the technology of the present invention is used, for example, as stationary power generation equipment for industrial use and consumer use.

【００１２】本発明の実施の形態の一例を図１〜図８を
参照して説明する。図１及び図２は本発明に係るシート
リング１の形状を示す。シートリング１は、シリンダヘ
ッドに開口した吸気ポートの開口に装着される。シート
リング１は、吸気ポートの側に開口した孔部２を有する
入り口部３と、燃焼室側に設けられて吸気弁が接触する
シート面４を有する弁座部５と、シリンダヘッドの開口
に装着するための嵌め込み部６等から構成されている。An embodiment of the present invention will be described with reference to FIGS. 1 and 2 show the shape of a seat ring 1 according to the present invention. The seat ring 1 is mounted in an opening of an intake port opened in a cylinder head. The seat ring 1 has an inlet 3 having a hole 2 opened to the intake port side, a valve seat 5 provided on the combustion chamber side and having a seat surface 4 with which an intake valve comes into contact, and an opening in the cylinder head. It is composed of a fitting part 6 for mounting.

【００１３】シートリング１は同芯円加工ではなく、外
径の中心と、孔部２の内径の中心が一致していない。即
ち偏芯している。孔部２の内周面は、外径の中心ａから
Ｅだけ偏芯した中心ｂを有する内径φＢの周面からな
る。ここで、外径の中心ａから内径の中心ｂに向かう方
向を、シートリング１の偏芯方向と呼ぶ。このような偏
芯した孔部２を得るには、外径の中心ａを有する内径φ
Ａの周面を形成し、その後に内径φＢの周面を加工す
る。その結果、図１に示すように、シートリング１の孔
部２の内周面の内、シートリング１の偏芯方向について
後方の部分は、内径φＡの周面を形成した際の凸状周面
２ａを維持するが、それ以外のシートリング１の偏芯方
向について前方の部分は平坦周面２ｂとなる。The center of the outer diameter of the seat ring 1 is not concentric, and the center of the inner diameter of the hole 2 does not coincide. That is, it is eccentric. The inner peripheral surface of the hole 2 is formed of a peripheral surface having an inner diameter φB having a center b eccentric by E from the center a of the outer diameter. Here, the direction from the center a of the outer diameter to the center b of the inner diameter is referred to as an eccentric direction of the seat ring 1. In order to obtain such an eccentric hole 2, an inner diameter φ having a center a of the outer diameter is used.
A peripheral surface of A is formed, and thereafter, a peripheral surface of the inner diameter φB is processed. As a result, as shown in FIG. 1, of the inner peripheral surface of the hole 2 of the seat ring 1, the rear part in the eccentric direction of the seat ring 1 has a convex peripheral portion when the peripheral surface of the inner diameter φA is formed. The surface 2a is maintained, but the other portion in the eccentric direction of the seat ring 1 becomes a flat peripheral surface 2b.

【００１４】この偏芯シートリング１の偏芯方向をシリ
ンダヘッドの吸気ポート形状に対して最適な配置で装着
することにより、スワール比と流量係数という相反要素
の両立を可能とした。By mounting the eccentric seat ring 1 in an eccentric direction that is optimal for the shape of the intake port of the cylinder head, reciprocal factors such as a swirl ratio and a flow coefficient can be achieved.

【００１５】図３は、エンジンのシリンダヘッドにおけ
る吸気弁と排気弁の配置を示す平面図である。図示のよ
うに、このエンジンは吸気弁（ＩＶ，ＩＧＶに装着）と
排気弁（ＥＶに装着）を２個ずつ有している。図中破線
で示す吸気ポート１０において、２個の開口が吸気の流
れに対して上流と下流の２つの位置にそれぞれ配置され
ている。上流の開口を記号ＩＧＶ（ポートＡ）と呼び、
下流の開口を記号ＩＶ（ポートＢ）と呼ぶ。FIG. 3 is a plan view showing the arrangement of the intake valve and the exhaust valve in the cylinder head of the engine. As shown, this engine has two intake valves (mounted on IV and IGV) and two exhaust valves (mounted on EV). In the intake port 10 indicated by a broken line in the figure, two openings are respectively arranged at two positions upstream and downstream with respect to the flow of intake air. The upstream opening is called a symbol IGV (port A),
The downstream opening is referred to as symbol IV (port B).

【００１６】ここで、吸気方向に対するシートリング１
の偏芯方向を規定するため、図３の平面図において時計
の時方位を用いる。即ち、図３において上向きの方向を
１２時とし、右向きの方向を３時とし、下向きの方向を
６時とし、左向きの方向を９時とする。従って、吸気ポ
ート１０における吸気の流れの方向は略１２時である。Here, the seat ring 1 with respect to the intake direction
In order to define the eccentric direction, the time orientation of the watch is used in the plan view of FIG. That is, in FIG. 3, the upward direction is 12:00, the rightward direction is 3 o'clock, the downward direction is 6 o'clock, and the leftward direction is 9 o'clock. Therefore, the flow direction of the intake air at the intake port 10 is approximately 12:00.

【００１７】（１）偏芯シートリング１のスワール比と
流量係数 次に、本例のシートリング１を種々の偏芯方向でシリン
ダヘッドに装着した複数の例と、偏芯していない従来の
シートリング１を用いた例について、羽根車を用いた定
常流試験装置を用いてスワール強さと流量係数を比較し
た。この実験で使用した偏芯シートリング１は、内径φ
６４ｍｍを３ｍｍ偏芯させて内径φ７０ｍｍで加工した
ものである。図４は、定常流試験における標準（従来
例）シートリング１と、偏芯シートリング１の偏芯方向
の組み合わせを示す。ここで符号Ａに付した数字は、偏
芯方向の時方位を示す。例えばテストＮｏ．２のＩＧＶ
では、偏芯方向は２時の方向である。(1) Swirl ratio and flow coefficient of eccentric seat ring 1 Next, a plurality of examples in which the seat ring 1 of this embodiment is mounted on a cylinder head in various eccentric directions, and a conventional example in which the eccentric seat ring is not eccentric. For the example using the seat ring 1, the swirl strength and the flow coefficient were compared using a steady flow test device using an impeller. The eccentric seat ring 1 used in this experiment has an inner diameter φ
It is formed by eccentricizing 64 mm by 3 mm and processing with an inner diameter of 70 mm. FIG. 4 shows a combination of a standard (conventional example) seat ring 1 and an eccentric seat ring 1 in an eccentric direction in a steady flow test. Here, the number attached to the symbol A indicates the azimuth of the eccentric direction. For example, test No. 2 IGV
Then, the eccentric direction is the direction of 2 o'clock.

【００１８】実験結果を図５に示す。テストＮｏ．１の
従来例を基準に考えると、テストＮｏ．２の本シートリ
ング１の取り付け方向はスワール比、流量係数共に低下
し、本願の意図する効果が得られない。FIG. 5 shows the experimental results. Test No. Considering the conventional example of Test No. 1 as a reference, Test No. In the mounting direction of the second seat ring 1, both the swirl ratio and the flow coefficient decrease, and the effect intended by the present application cannot be obtained.

【００１９】テストＮｏ．３では他のテストと逆回りの
スワールが発生している。これは偏芯方向先側の内壁が
直線的（平面的）に加工してあるのに対して、反対側は
半月形状（凸周形状）をしており、このため半月形の方
の流速が増加し、逆回りのスワールになったと考えられ
る。Test No. In No. 3, a swirl reverse to that of the other tests occurred. This is because the inner wall on the leading side in the eccentric direction is machined linearly (planar), while the other side has a semi-lunar shape (convex peripheral shape). It is thought that the swirl increased in the opposite direction.

【００２０】以上の結果から、偏芯方向をスワールを発
生させたい方向と１８０°の方向にして組み込んだもの
がテストＮｏ．４とＮｏ．５である。ここでは、ポート
Ａからの空気をシリンダライナ壁にぶつける方向のテス
トＮｏ．４の方が、流量係数は同等であるが、高いスワ
ール数を得た。From the above results, Test No. 1 was incorporated with the eccentric direction set to the direction in which swirl was generated and the direction of 180 °. 4 and No. 5 Here, the test No. in the direction in which the air from the port A hits the cylinder liner wall. No. 4 had the same flow coefficient, but obtained a high swirl number.

【００２１】（２）単気筒エンジンによる燃焼と性能試
験 ａ）試験条件 偏芯シートリング１とその組み込み方向をテストＮｏ．
４の状態として、シリンダ径２６０ｍｍの単シリンダ火
花点火ガスエンジンにより試験を実施した。 （３）試験結果 ａ）燃焼に与える影響 図６に排気中の残存酸素濃度（以下Ｏ2 濃度と記す）、
初期燃焼期間（０−５％熱発生期間）および燃焼期間
（５−９５％熱発生期間）の関係を示す。熱発生解析に
は主燃焼室内の圧力計測値を用いた。図６からスワール
を強くしても０−５％熱発生期間の差はほとんどない
が、燃焼期間はスワールを強くすると短くなっているこ
とがわかる。特にＯ2 濃度を大きくした場合に短期燃焼
の傾向が強い。(2) Combustion and performance test using a single cylinder engine a) Test conditions Test No.
In the state of No. 4, the test was performed using a single cylinder spark ignition gas engine having a cylinder diameter of 260 mm. (3) Test results a) referred to as the residual oxygen concentration (hereinafter O 2 concentration in the exhaust gas to effect 6 given to combustion),
The relationship between the initial combustion period (0-5% heat generation period) and the combustion period (5-95% heat generation period) is shown. The pressure measurement in the main combustion chamber was used for the heat generation analysis. It can be seen from FIG. 6 that there is almost no difference in the 0-5% heat generation period even if the swirl is increased, but the combustion period becomes shorter as the swirl is increased. In particular, when the O 2 concentration is increased, the tendency of short-term combustion is strong.

【００２２】ｂ）排ガス性状に与える影響 図７はスワール強さを変えた場合のＯ2 濃度とＮＯｘ、
ＣＯ、ＴＨＣ濃度の関係を示す。同一Ｏ2 濃度ではスワ
ールを強くした方がＮＯｘ濃度が高くなる。ＮＯｘ濃度
の上昇率はＯ2 濃度が小さいほど大きい。例えばＯ2 濃
度１３．５％近辺ではＮＯｘ濃度の差は１０ｐｐｍ程度
と小さく、Ｏ2 濃度１２．５％では約７０ｐｐｍであ
る。スワールを強化した時はＯ2 濃度１２．４％がノッ
キング発生限界であった。B) Effect on Exhaust Gas Properties FIG. 7 shows the relationship between the O 2 concentration and NOx, when the swirl strength is changed.
4 shows the relationship between CO and THC concentrations. Who was strongly swirl the higher the NOx concentration in the same O 2 concentration. Increase rate of NOx concentration is greater as the O 2 concentration is low. For example, when the O 2 concentration is around 13.5%, the difference in NOx concentration is as small as about 10 ppm, and when the O 2 concentration is 12.5%, it is about 70 ppm. When the swirl was strengthened, the O 2 concentration of 12.4% was the knocking occurrence limit.

【００２３】ＣＯ濃度はスワールを強くすると低下す
る。特にＯ2 濃度が小さくなるほど低減率が大きい。例
えばＯ2 濃度１２．５％〜１３．０％の場合では約２０
０ｐｐｍ低下する。The CO concentration decreases with increasing swirl. In particular, the lower the O 2 concentration, the greater the reduction rate. For example, when the O 2 concentration is 12.5% to 13.0%, about 20
It is reduced by 0 ppm.

【００２４】ＴＨＣ濃度はスワールを強くすると全ての
Ｏ2 濃度範囲で下がる。Ｏ2 濃度が小さくなるほど低減
量は大きくなるが、おおむね０．２〜０．３％（Ｏ2 ０
％換算濃度値）低くなる。When the swirl is increased, the THC concentration decreases in the entire O 2 concentration range. As the O 2 concentration decreases, the amount of reduction increases, but it is approximately 0.2 to 0.3% (O 20
% Converted concentration value).

【００２５】ｃ）燃料消費率とＮＯｘに与える影響 図８に燃料消費率とＮＯｘ濃度の関係を示す。ＮＯｘ濃
度を同一として燃料消費率を比較するとスワールを強く
した方が良いことがわかる。この理由は、ＮＯｘ濃度２
００ｐｐｍレベルの希薄混合気の燃焼であるため断熱火
炎温度が低く、ＮＯｘ濃度の上昇率は小さい。一方、燃
焼促進によるＴＨＣ濃度の改善効果が大きく、その結果
燃料消費率が改善されたものと考えられる。C) Effect on fuel consumption rate and NOx FIG. 8 shows the relationship between the fuel consumption rate and the NOx concentration. Comparing the fuel consumption rates with the same NOx concentration shows that it is better to increase the swirl. The reason is that NOx concentration 2
Since the combustion is a lean mixture at a level of 00 ppm, the adiabatic flame temperature is low, and the rate of increase in the NOx concentration is small. On the other hand, it is considered that the effect of improving the THC concentration by promoting combustion is large, and as a result, the fuel consumption rate has been improved.

【００２６】（４）まとめ 以上の実験結果から次のことがわかる。スワールを強く
すると燃焼期間は短くなる。特にＯ2 濃度を大きくした
場合、つまり空気過剰率を大きくする場合に短期燃焼化
の傾向が強い。これには、次の各点が理由として考えら
れる。 乱れのエネルギーが燃焼を活性化し燃焼速度が速く
なる。 乱れにより混合気の濃度分布（均一性）が変化し燃
焼速度が速くなる。 その結果、ＣＯ・ＴＨＣ濃度の低減効果が得られ燃料消
費率も改善される。(4) Summary The following is clear from the above experimental results. Increasing the swirl shortens the combustion period. In particular, when the O 2 concentration is increased, that is, when the excess air ratio is increased, the tendency of short-term combustion is strong. The following points can be considered as reasons for this. The turbulent energy activates the combustion and increases the burning speed. The turbulence changes the concentration distribution (uniformity) of the air-fuel mixture and increases the combustion speed. As a result, the effect of reducing the CO / THC concentration is obtained, and the fuel consumption rate is also improved.

【００２７】このような結果を得るためには、シートリ
ングの形状・構造と、これをシリンダヘッドに取り付け
る際の向きは、次の条件を満たすことが必要と考えられ
る。まず、スワール強化のためには、シートリング１の
中央に開口した孔部２の内径の中心が、外径の中心に対
して偏芯していることが必要である。次に、シートリン
グ１の偏芯方向が、吸気ポート１０から燃焼室に供給さ
れる吸気の方向に対して略反対向きとなるように、シー
トリング１を開口に取り付けることが必要である。In order to obtain such a result, it is considered necessary that the shape and structure of the seat ring and the orientation when the seat ring is mounted on the cylinder head satisfy the following conditions. First, in order to strengthen the swirl, the center of the inner diameter of the hole 2 opened at the center of the seat ring 1 needs to be eccentric with respect to the center of the outer diameter. Next, it is necessary to attach the seat ring 1 to the opening such that the eccentric direction of the seat ring 1 is substantially opposite to the direction of intake air supplied from the intake port 10 to the combustion chamber.

【００２８】特に、２つのポートを有する場合には、吸
気ポートから吸入される吸気の流れの方向を１２時とし
た場合、この流れに沿って上流側のシートリング１の偏
芯方向を６時から９時の角度範囲に設定し、この流れに
沿って下流側のシートリング１の偏芯方向を３時から６
時の角度範囲に設定すると、前述したテストＮｏ．４又
は５のような好結果が得られる。In particular, in the case of having two ports, if the direction of the flow of the intake air sucked from the intake port is 12:00, the eccentric direction of the upstream seat ring 1 along this flow is 6:00. From 9 o'clock to 9 o'clock, and the eccentric direction of the seat ring 1 on the downstream side along this flow from 3 o'clock to 6 o'clock.
When the angle range is set to the time range of the test No. Good results such as 4 or 5 are obtained.

【００２９】[0029]

【発明の効果】本発明によれば、シートリングの孔部の
内径の中心を外径の中心に対して偏芯させており、さら
に吸気ポートにおける吸気の方向に対して前記シートリ
ングの偏芯方向を所定の方向に設定しているので、スワ
ール比と流量係数について同時に十分な値を達成できる
という効果が得られる。According to the present invention, the center of the inner diameter of the hole of the seat ring is eccentric with respect to the center of the outer diameter, and the eccentricity of the seat ring with respect to the direction of intake air at the intake port. Since the direction is set to the predetermined direction, an effect that a sufficient value can be achieved simultaneously for the swirl ratio and the flow coefficient can be obtained.

【図面の簡単な説明】[Brief description of the drawings]

【図１】本発明の実施の形態の一例であるシートリング
の図２の切断線（イ）における断面図である。FIG. 1 is a sectional view of a seat ring according to an embodiment of the present invention, taken along section line (a) of FIG.

【図２】本発明の実施の形態の一例であるシートリング
の平面図である。FIG. 2 is a plan view of a seat ring as an example of the embodiment of the present invention.

【図３】本発明の実施の形態の一例において、シリンダ
ヘッドにおける吸気ポート等の配置と、シートリングの
回転方向の配置を示す平面図である。FIG. 3 is a plan view showing an arrangement of intake ports and the like in a cylinder head and an arrangement of a seat ring in a rotation direction in an example of an embodiment of the present invention.

【図４】本発明の実施の形態の一例において行った試験
のシリンダヘッドの種類と偏芯方向の向きの組み合わせ
を示した表図である。FIG. 4 is a table showing combinations of types of cylinder heads and eccentric directions in a test performed in an example of an embodiment of the present invention.

【図５】本発明の実施の形態の一例においてテストＮ
ｏ．１〜５について測定したスワール強さと流量係数を
示す表図である。FIG. 5 shows a test N according to an embodiment of the present invention.
o. It is a table | surface figure which shows the swirl intensity and the flow coefficient measured about 1-5.

【図６】本発明の実施の形態の一例において行った試験
の結果を示すものであり、排気中の残存酸素濃度、初期
燃焼期間および燃焼期間の関係を示す表図である。FIG. 6 is a table showing a result of a test performed in an example of the embodiment of the present invention, and showing a relationship among a residual oxygen concentration in exhaust gas, an initial combustion period, and a combustion period.

【図７】本発明の実施の形態の一例において行った試験
の結果を示すものであり、スワール強さを変えた場合の
Ｏ2 濃度とＮＯｘ、ＣＯ、ＴＨＣ濃度の関係を示す表図
である。FIG. 7 is a table showing the results of a test performed in an example of the embodiment of the present invention, and showing the relationship between the O 2 concentration and the NOx, CO, and THC concentrations when the swirl strength is changed. .

【図８】本発明の実施の形態の一例において行った試験
の結果を示すものであり、燃料消費率とＮＯｘ濃度の関
係を示す表図である。FIG. 8 is a table showing a result of a test performed in an example of the embodiment of the present invention and showing a relationship between a fuel consumption rate and a NOx concentration.

【図９】従来のシートリングの断面図である。FIG. 9 is a sectional view of a conventional seat ring.

【符号の説明】[Explanation of symbols]

１ シートリング ２ 孔部 １０ 吸気ポート DESCRIPTION OF SYMBOLS 1 Seat ring 2 Hole 10 Intake port

Claims (5)

【特許請求の範囲】[Claims] 【請求項１】 内燃機関の燃焼室に連通する吸気ポート
の開口に取り付けられ、前記給気ポートの開口を開閉す
る吸気弁が当接するシートリングにおいて、中央に開口
した孔部の内径の中心が、外径の中心に対して偏芯して
いることを特徴とする給気弁のシートリング。1. A seat ring, which is attached to an opening of an intake port communicating with a combustion chamber of an internal combustion engine and abuts an intake valve that opens and closes the opening of the air supply port, has a center of an inner diameter of a hole opened at the center. A seat ring of the air supply valve, wherein the seat ring is eccentric with respect to the center of the outer diameter. 【請求項２】 前記外径の中心から前記内径の中心に向
かう前記シートリングの偏芯方向が、前記吸気ポートか
ら前記燃焼室に供給される吸気の方向に対して略反対向
きとなるように、前記シートリングを前記開口に取り付
けたことを特徴とする請求項１記載の吸気弁のシートリ
ング。2. The eccentric direction of the seat ring from the center of the outer diameter toward the center of the inner diameter is substantially opposite to the direction of intake air supplied from the intake port to the combustion chamber. 2. The seat ring for an intake valve according to claim 1, wherein said seat ring is attached to said opening. 【請求項３】 前記シートリングの前記孔部の内周面の
内、前記シートリングの偏芯方向について前方の部分
が、前記開口部の中心軸と平行な平面における断面で直
線状を呈し、かつ前記シートリングの偏芯方向について
後方の部分が、前記開口部の中心軸と平行な平面におけ
る断面で円周状を呈するように構成したことを特徴とす
る請求項１記載の吸気弁のシートリング。3. An inner peripheral surface of the hole of the seat ring, wherein a portion in front of the eccentric direction of the seat ring has a linear shape in a cross section in a plane parallel to a central axis of the opening, 2. The seat for an intake valve according to claim 1, wherein a portion rearward in the eccentric direction of the seat ring has a circumferential shape in a cross section in a plane parallel to a central axis of the opening. ring. 【請求項４】 内燃機関の燃焼室に連通する吸気ポート
の２つの開口に取り付けられ、前記各開口を開閉する２
つの吸気弁がそれぞれ当接する２つのシートリングにお
いて、各シートリングともに中央に開口した孔部の内径
の中心が外径の中心に対して偏芯しており、前記外径の
中心から前記内径の中心に向かう方向を前記シートリン
グの偏芯方向とし、かつ前記吸気ポートから吸入される
吸気の流れの方向を１２時とした場合、前記流れに沿っ
て上流側のシートリングの偏芯方向が６時から９時の角
度範囲に設定され、前記流れに沿って下流側のシートリ
ングの偏芯方向が３時から６時の角度範囲に設定された
吸気弁のシートリング。4. An intake port, which is attached to two openings of an intake port communicating with a combustion chamber of an internal combustion engine, and opens and closes each of the openings.
In the two seat rings that the two intake valves respectively contact, the center of the inner diameter of the hole opened at the center of each of the seat rings is eccentric with respect to the center of the outer diameter, and the center of the outer diameter is smaller than the center of the inner diameter. When the direction toward the center is the eccentric direction of the seat ring, and the direction of the flow of the intake air taken from the intake port is 12:00, the eccentric direction of the upstream seat ring along the flow is 6 o'clock. The seat ring of the intake valve, wherein the seat ring of the intake valve is set in the angle range from 3 o'clock to 9 o'clock, and the eccentric direction of the downstream seat ring along the flow is set in the angle range from 3 o'clock to 6 o'clock. 【請求項５】 請求項１又は２又は３又は４記載の吸気
弁のシートリングを備えたガスエンジン。5. A gas engine comprising the intake valve seat ring according to claim 1, 2, 3 or 4.
JP19589698A 1998-07-10 1998-07-10 Intake valve seat ring and gas engine Expired - Lifetime JP3715437B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP19589698A JP3715437B2 (en) 1998-07-10 1998-07-10 Intake valve seat ring and gas engine

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP19589698A JP3715437B2 (en) 1998-07-10 1998-07-10 Intake valve seat ring and gas engine

Publications (2)

Publication Number Publication Date
JP2000027612A true JP2000027612A (en) 2000-01-25
JP3715437B2 JP3715437B2 (en) 2005-11-09

Family

ID=16348801

Family Applications (1)

Application Number Title Priority Date Filing Date
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Country Link
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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003069147A1 (en) * 2000-08-14 2003-08-21 Niigata Power Systems Co., Ltd. Cylinder head
KR100827831B1 (en) 2002-02-13 2008-05-07 니이가타 겐도키 가부시키가이샤 Cylinder head
AT501934B1 (en) * 2006-08-28 2008-05-15 Avl List Gmbh Gas exchange duct for a combustion engine
JP2015068259A (en) * 2013-09-30 2015-04-13 本田技研工業株式会社 Cylinder head, and processing method of cylinder head
US20150219006A1 (en) * 2012-08-17 2015-08-06 Caterpillar Energy Solutions Gmbh Cylinder head with countersink

Families Citing this family (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US10934899B2 (en) 2018-11-13 2021-03-02 Caterpillar Inc. Valve seat insert for engine having double-crowned seating surface profiled for limiting valve recession
US11060425B2 (en) 2019-03-13 2021-07-13 Caterpillar Inc. Valve seat insert for engine head having venturi flow crowns and seating surface profiled for limiting valve recession
US10989321B2 (en) 2019-04-26 2021-04-27 Caterpillar Inc. Double-crowned valve seat insert having seating surface formed of hard-facing material

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2003069147A1 (en) * 2000-08-14 2003-08-21 Niigata Power Systems Co., Ltd. Cylinder head
CN100458132C (en) * 2000-08-14 2009-02-04 新泻原动机株式会社 Cylinder head
KR100827831B1 (en) 2002-02-13 2008-05-07 니이가타 겐도키 가부시키가이샤 Cylinder head
AT501934B1 (en) * 2006-08-28 2008-05-15 Avl List Gmbh Gas exchange duct for a combustion engine
US20150219006A1 (en) * 2012-08-17 2015-08-06 Caterpillar Energy Solutions Gmbh Cylinder head with countersink
JP2015068259A (en) * 2013-09-30 2015-04-13 本田技研工業株式会社 Cylinder head, and processing method of cylinder head

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