JPS60142016A - Two-valve intake port for internal combustion engines - Google Patents
Two-valve intake port for internal combustion enginesInfo
- Publication number
- JPS60142016A JPS60142016A JP58245762A JP24576283A JPS60142016A JP S60142016 A JPS60142016 A JP S60142016A JP 58245762 A JP58245762 A JP 58245762A JP 24576283 A JP24576283 A JP 24576283A JP S60142016 A JPS60142016 A JP S60142016A
- Authority
- JP
- Japan
- Prior art keywords
- intake
- valve
- intake port
- port
- boat
- 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.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 title claims description 10
- 241001062872 Cleyera japonica Species 0.000 claims 1
- 238000010586 diagram Methods 0.000 description 6
- 230000007423 decrease Effects 0.000 description 3
- 239000013078 crystal Substances 0.000 description 1
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F1/42—Shape or arrangement of intake or exhaust channels in cylinder heads
- F02F1/4235—Shape or arrangement of intake or exhaust channels in cylinder heads of intake channels
-
- 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
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
-
- 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
- F02B31/00—Modifying induction systems for imparting a rotation to the charge in the cylinder
- F02B31/08—Modifying induction systems for imparting a rotation to the charge in the cylinder having multiple air inlets
- F02B31/085—Modifying induction systems for imparting a rotation to the charge in the cylinder having multiple air inlets having two inlet valves
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02F—CYLINDERS, PISTONS OR CASINGS, FOR COMBUSTION ENGINES; ARRANGEMENTS OF SEALINGS IN COMBUSTION ENGINES
- F02F1/00—Cylinders; Cylinder heads
- F02F1/24—Cylinder heads
- F02F2001/244—Arrangement of valve stems in cylinder heads
- F02F2001/247—Arrangement of valve stems in cylinder heads the valve stems being orientated in parallel with the cylinder axis
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Chemical & Material Sciences (AREA)
- Combustion & Propulsion (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cylinder Crankcases Of Internal Combustion Engines (AREA)
Abstract
(57)【要約】本公報は電子出願前の出願データであるた
め要約のデータは記録されません。(57) [Summary] This bulletin contains application data before electronic filing, so abstract data is not recorded.
Description
【発明の詳細な説明】
本発明は、内燃機関の低速運転時に第７吸気ボートを使
用し、高速運転時に第１と第２の両吸気ポートを使用す
る２弁式吸気ポートに関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a two-valve intake port that uses the seventh intake boat during low-speed operation of an internal combustion engine and uses both the first and second intake ports during high-speed operation.
従来のこの種の２弁式殺気ポートは、第１図に示すよう
に、第１吸気ボートに強い渦流を生起させるヘリカルポ
ート（１）を用い、第２吸気ボートに圧力損失の少ない
ダイレクショナルポート（２） ヲ用いており、低速運
転時にはへりカルポート（１）によって強い渦流を生起
させ、高速運転時にはダイレクショナルポート（２）と
へりカルポート（１）によって高い体積効率を得ること
を目的としている。ところが、その目的が充分に達成さ
れているとは言い難く、特１（低速運転時における渦流
の強さが充分ではない。As shown in Figure 1, this type of conventional two-valve killing port uses a helical port (1) that creates a strong vortex in the first intake boat, and a directional port with less pressure loss in the second intake boat. (2) The aim is to generate a strong vortex by the helical port (1) during low-speed operation, and to obtain high volumetric efficiency using the directional port (2) and helical port (1) during high-speed operation. However, it is difficult to say that this objective has been fully achieved, and Special 1 (the strength of the vortex flow during low-speed operation is not sufficient).
本発明の目的は、上記のような従来の欠点をなくし、低
速運転時に強い渦流を、高速運転時の体積効率を犠牲に
することなく、生起させることかでさる内燃機関の２弁
式吸気ポートを提供することである。The purpose of the present invention is to eliminate the above-mentioned conventional drawbacks and to provide a two-valve intake port for an internal combustion engine that generates a strong vortex flow during low-speed operation without sacrificing volumetric efficiency during high-speed operation. The goal is to provide the following.
本発明者は、上記のような従来の欠点の原因は、第１吸
気ポートの吸気孔が第２吸気ボートのそれと同径であり
、また、嘱／吸気ポートがへりカルホードである点に１
６眼し、第１吸気ポートの吸気孔を第」吸気ポートのそ
れより大径に形成し、塘だ、第１吸気ポートに、以ｎｉ
ｌ Ｋ発明したオフセットボートとも言９べき、へりカ
ルポートとタンジエンシャルポートの中１川の形状全し
た吸気ポートな用いてみたところ、優れた性能を示した
のである。The inventor of the present invention believes that the causes of the above-mentioned conventional drawbacks are that the intake hole of the first intake port has the same diameter as that of the second intake boat, and that the intake port is helical.
6, the intake hole of the first intake port is formed to have a larger diameter than that of the 2nd intake port.
It can be said that the offset boat was invented by K, and when we used the intake port in the shape of a helical port and a tangential port, it showed excellent performance.
即ち、本発明は、シリンダ室の端■にその中心から偏芯
した２個所の位置にそれぞれ吸気孔を開口し、両吸気孔
にそれぞれ吸気弁を設けると共に吸気通路を接続して、
第１と第２の２個の吸気ポートを形成し、低速運転時に
第７吸気ポートを使用し、高速運転時に第１と第２の両
吸気ボートを使用ｒる内燃機関の２弁式吸気ポートにお
いて、＠／吸気ポートの吸気孔を第２吸気ボートのそれ
より大径に形成し、第１吸気ポートの吸気通路を、吸気
孔に連通して吸気弁を囲む通路端の渦流生起部とこの通
路端以外の導入部から構成し、第１吸気ポートの吸気弁
め弁軸周面とこれに対面した渦流生起部の局面間の幅を
、シリンダ室周面（ｔｉｌｌの外側部分ではシリンダ室
中・Ｄ （Ｈｌｌの内側部分より広くし、渦流生起部の
外側部分に導入部を接続し、第１吸気ポートの吸気孔の
開口面とこれに対面した渦流生起部の天井間の高さを、
弁軸の回りに幅広の外側部分から幅狭の内側部分に至る
間に減少させ、その平均減少量を弁軸の回りに７度当り
吸気孔の径の０５以上で０７ｇ％以下に設定したことを
特徴とする内燃機関の２弁式吸気ポートである。That is, in the present invention, intake holes are opened at two positions eccentric from the center of the cylinder chamber at the end (2), intake valves are provided in both intake holes, and intake passages are connected to each other.
A two-valve intake port for an internal combustion engine that forms two intake ports, the first and second, and uses the seventh intake port during low-speed operation and uses both the first and second intake ports during high-speed operation. In this case, the intake hole of the intake port is formed to have a larger diameter than that of the second intake boat, and the intake passage of the first intake port is connected to the vortex generating portion at the end of the passage that communicates with the intake port and surrounds the intake valve. The width between the circumferential surface of the intake valve shaft of the first intake port and the surface of the vortex generating portion facing the first intake port is defined as the width between the circumferential surface of the cylinder chamber (in the outside part of the till, the width is within the cylinder chamber).・D (Wider than the inner part of the Hll, connect the introduction part to the outer part of the vortex generating part, and set the height between the opening surface of the intake hole of the first intake port and the ceiling of the vortex generating part facing this,
It is reduced from the wide outer part to the narrow inner part around the valve stem, and the average reduction amount is set to 0.05 g% or less of the intake hole diameter per 7 degrees around the valve stem and 0.7 g% or less. This is a two-valve intake port for an internal combustion engine.
この２弁式吸気ポートにおいては、後記する実験結果か
ら明らかなように、低速運転時に強い渦流を生起させる
ことができ、普だ、そのために高速運転時の体積効率が
犠牲にならない。In this two-valve intake port, as is clear from the experimental results described later, it is possible to generate a strong vortex flow during low-speed operation, and the volumetric efficiency during high-speed operation is not sacrificed because of this.
次に、本発明の実施例について説明する。Next, examples of the present invention will be described.
第１実施例（第２図と第３図参照）
本例の内燃機関のノ弁式吸気ポートは、第２図に示すよ
りに、シリンダ室０］）の円形端面にその［ヤＩしから
周辺の一側に偏芯した２個所の位置にそれぞれ大径（３
０門）、小径（コ２ガＭ）の吸気孔（鵡翰を開口し、両
吸気孔（１；６ 、 ＠にそれぞれ７１セべ・ソト成し
ている。なお、第１吸気ポートの吸気孔ｑ４は第２吸気
ボートの吸気孔（イ）より大径であるが、両吸気孔（１
カ、（２）の開口面積の和は従来におけるのと同一であ
る。第２吸気ボートいは従来におけるのト同様にダイレ
クショナルポートとし、第１吸気ポート０（）は新規な
オフセットポートとしている。1st Embodiment (See Figures 2 and 3) As shown in Figure 2, the valve-type intake port of the internal combustion engine of this example is located at the circular end face of the cylinder chamber 0). There are two large diameter (3
0 gate), a small diameter (Ko 2 Ga M) intake hole (Pink) is opened, and both intake holes (1; 6, @ are each 71 cm. Hole q4 has a larger diameter than the intake hole (a) of the second intake boat, but both intake holes (1
F. The sum of the opening areas in (2) is the same as in the prior art. The second intake port is a directional port like the conventional one, and the first intake port 0() is a new offset port.
このオフセットボー） Ｑ（］は、吸気通路Ｏｎを、’
１％孔０ｚに連通してφ啓吸気弁ｕ４を囲む通路端の渦
流生起部ｕＱとこの通路端以外の導入部０１から構成し
。This offset bow) Q(] is the intake passage On, '
It consists of a vortex generating part uQ at the end of the passage communicating with the 1% hole 0z and surrounding the φ air intake valve u4, and an introduction part 01 other than the end of the passage.
７１Ｚ、＼流牛起部囮の周面を、吸気弁の弁ｆｉ（１４
１０周面に対面した２枚の円筒面を滑らかに接続して形
成し。71Z, the circumferential surface of the flow cow origin decoy is attached to the valve fi (14) of the intake valve.
10 It is formed by smoothly connecting two cylindrical surfaces facing each other.
弁軸０４１の周面とこれに対面化た渦流生起部ＯＱの周
面間の幅を、シリンダ室（１１）局面側の外側部分０７
ノではシリンダ室中Ｉｂ側の内側部分α印より広くして
、弁軸圓の回りに外側部分（１７）力・ら内側部分（１
８＋に至る間に徐々に狭くし、渦流生起部ＯＱの幅広の
外側部分りηにその接線方向に沿って直線状の導入部ｕ
特を接続し、吸気孔ｕ′４の開口面とされに対面した渦
流生起部四の天井間の高さを、弁ｆｌｔｔｂ （Ｉ４の
回りにｌ１１晶広の外側部分（ｌηから幅狭の内側部分
ｕ８）に至る間に同一とし又は徐々に減少させ、その減
少量を弁軸（Ｉ４）の回りに７度当り吸気孔ａカの径の
０７ｇ％以内に設定している。The width between the circumferential surface of the valve shaft 041 and the circumferential surface of the vortex generating portion OQ facing the valve shaft 041 is determined by the outer portion 07 on the side of the cylinder chamber (11).
, the inner part (17) on the Ib side of the cylinder chamber is made wider than the mark α, and the inner part (17) is applied around the valve shaft circle.
While reaching 8+, the width is gradually narrowed, and a linear introduction part u is formed along the tangential direction of the wide outer part η of the vortex generating part OQ.
The height between the opening surface of the intake hole U'4 and the ceiling of the vortex generating part 4 facing the valve flttb (around I4 is the wide outer part of l11 crystal (from lη to the narrow inner part) u8) is kept the same or gradually decreases, and the amount of decrease is set within 07g% of the diameter of the intake hole a per 7 degrees around the valve shaft (I4).
本例の２弁式吸気ボートにおいては、内Ｆ１機関の低速
運転時に第１吸気ポートのオフセットボート四を使用し
、高速運転時にオフセ゛ソトｄ＃−）（１（１の外に第
２吸気ボートのダイレクショナルポート四もイ吏用する
。In the two-valve intake boat of this example, offset boat 4 of the first intake port is used during low-speed operation of the internal F1 engine, and offset boat 4 of the first intake port is used during high-speed operation. Directional port 4 is also used.
ダイレクショナルボート団における吸気の流れ方は従来
におけるのと同様である。The flow of intake air in directional boat fleets is similar to that in conventional boats.
オフセットポートθＱにおいては、吸気通路α９を流れ
る吸気は、導入部（１９から渦流生起部ｔｍに流入し、
吸気孔（１〕を経てシリンダ室（１１１に流入し、１だ
、吸気の主流は、導入部（ＩＩＪＱ軸芯位置から渦流生
起部の外側部分０７）の周面と弁軸（Ｉ４）の周面間の
中間位置に流入し、吸気孔（功を経てシリンダ室０１）
に流入し、−シリンダ室ＯＤの周面に沿って旋回する渦
流となる。In the offset port θQ, the intake air flowing through the intake passage α9 flows from the introduction part (19) into the vortex generation part tm,
The main flow of the intake air flows into the cylinder chamber (111) through the intake hole (1), and the main flow of the intake air flows through the circumferential surface of the introduction section (from the IIJQ axis position to the outer part 07 of the vortex generation section) and the circumference of the valve shaft (I4). Flows into the intermediate position between the surfaces, and enters the intake hole (through the cylinder chamber 01)
- becomes a vortex swirling along the circumferential surface of the cylinder chamber OD.
本例の２弁式吸気ポートにおいて、内燃機関のクランク
軸の回転ＶｉＮと、シリンダ室ａυに生起する渦流の強
さ即ちスワール比Ｓ几、シリンダ室（ＩＩ）の体積効率
ＷＥの関係をめてみたところ、第３図の線図に実線で示
すよりな実験結果分書た。捷た、比較のため、第１図に
示した従来の２弁式吸気ボートにおいて、同様に上記の
関係をめてみたところ、同線図に破線で示すよつな実験
結果を得た。In the two-valve intake port of this example, the relationship between the rotation ViN of the crankshaft of the internal combustion engine, the strength of the vortex generated in the cylinder chamber aυ, that is, the swirl ratio S, and the volumetric efficiency WE of the cylinder chamber (II) will be explained. When I looked at it, I wrote the experimental results shown in the solid line in the diagram in Figure 3. For comparison, we similarly examined the above relationship in the conventional two-valve intake boat shown in Figure 1, and obtained experimental results as shown by the broken line in the same diagram.
同線図の上半部から明らかなように、本例の２弁式吸気
ポートは、従来のそれに比して、オフセットボー） １
．１１１のみが使用されて回転ｋ ＮがＲ以下である低
４４転時に、スワール比８凡が高く、強い渦流が生起す
る。As is clear from the upper half of the diagram, the two-valve intake port of this example has a lower offset bow than the conventional one.
．． At low 44 rotations when only 111 is used and the rotation kN is less than R, the swirl ratio is high, about 8, and a strong vortex is generated.
また、同線図の下半部から明らかなように、本例の２弁
式吸気ポートは、従来のそれに比して、オフセットポー
ト０（１トダイレクショナルボ−１・翰が使用されて回
転数Ｎがｎを紳える高速運転時に、体積効率ＶＢが低下
しない。Also, as is clear from the lower half of the diagram, the two-valve intake port of this example is different from the conventional one in that the offset port 0 (1 directional valve 1) is used and the rotation During high-speed operation where the number N is n, the volumetric efficiency VB does not decrease.
第２実施例（第を図参照）
本例の内燃機関の２弁式吸気ポートは、第ｑ図に示すよ
りに、第２吸気ポー１− Ｃ慢を第２吸気Ｊｆ） ｔｌ
［）のオフセットポートより小型のオフセットポートに
したものであり、第２吸気ポート（７）以外の部分は前
例におけるのと同様である。Second Embodiment (See Figure 2) The two-valve intake port of the internal combustion engine of this example is as shown in Figure q.
This is a smaller offset port than the offset port in [), and the parts other than the second intake port (7) are the same as in the previous example.
本例の２弁式吸気ボートは、前例のそれに比して、第１
と第２の両吸気ポー）（１Ｇ、（至）が使用される高速
運転時に、強い渦流が体積効率を低下させずに生起する
。The two-valve intake boat of this example is different from that of the previous example.
During high speed operation, when both intake ports (1G, (to)) are used, strong vortices occur without reducing the volumetric efficiency.
第１図は従来の２弁吸気ポートの略示横断平面図であり
、第２図は本発明の第１実施例の２弁式吸気ボートの略
示横断平面図、第３図は同ノ弁式吸気ポートにおける内
燃機関のクランク軸の回転数Ｎとスワール比ＳＲ又は体
積効率ＶＥの関係を示す線図であり、第グ図は第２実施
例の２弁式り気ボートの略ボ横断平面図である。
１Ｕ・・・ｌワ／吸気ボート、オフセットボー１・１１
・・・シリンダ室 １２・・・吸気孔１ろ・・・吸気弁
１４・・・弁 軸
１５・・・吸気通路 １６・・・渦流生起部１７・・・
外側部分 １８・・・内側部分１９・・・導入部
２’ （Ｊ・・・＠２吸気ポート、ダイレクショナルホ
ート２２・・・吸゛気孔 ２３・・・吸気弁２５・・・
吸気通路
６０・・・第２吸気Ｊｆ−ト、オフセットボート第１図
１′４ 図
１０FIG. 1 is a schematic cross-sectional plan view of a conventional two-valve intake port, FIG. 2 is a schematic cross-sectional plan view of a two-valve intake port according to the first embodiment of the present invention, and FIG. 2 is a diagram showing the relationship between the rotational speed N of the crankshaft of the internal combustion engine and the swirl ratio SR or volumetric efficiency VE at the intake port, and FIG. It is a diagram. 1U...l wa/intake boat, offset boat 1/11
... Cylinder chamber 12 ... Intake hole 1 ... Intake valve 14 ... Valve shaft 15 ... Intake passage 16 ... Vortex generating part 17 ...
Outer part 18...Inner part 19...Introduction part 2' (J...@2 intake port, directional port 22...Intake hole 23...Intake valve 25...
Intake passage 60...Second intake Jf-to, offset boat Fig. 1 1'4 Fig. 10
Claims (1)
にそれぞれ吸気孔を開口し、両級気孔にそれぞれ吸気弁
を設けると共に駁気通路を接続して、第１と第２の２個
の吸気ポートを形成し、低速運転時に第１吸気ボートを
使用し、高速運転時に第１と第コの両吸気ポートを使用
する内Ｐ機関の２弁式吸気ポートにおいて、第１吸気ポ
ートの吸気孔を第２吸気ボートの吸気孔より大径に形成
し、＠／吸気ボートの吸気通路を、吸気孔に連通して吸
気弁を囲む通路端の渦流生起部とこの通路端以外の導入
部から榊成し、第１吸気ボートの吸気弁の弁軸層１ｍと
これに対面した渦流生起部の周面１１１１の幅を、シリ
ンダ室周面側の外側部分ではシリンダ室中・ｕ１■１１
の内側部分より広くし、渦流生！田部の外側部分に導入
部を接続し、第１吸気ポートの吸気孔の開口面とこれに
対面した渦流生起部の天井°間の高さを、弁軸の回りに
幅広の外側部分から幅狭の内側部分に至る間に減少させ
、その平均減少量を弁軸の回りに７度当り吸気孔の径０
０％以上で０７ｇ％以下に設定したことを特徴とする内
燃機関の２弁式吸気ポート。Intake holes are opened at two positions eccentric from the center of the end face of the cylinder chamber, and intake valves are provided in each of the two class air holes, and an air passage is connected to the first and second two air holes. In a two-valve intake port of an inner P engine that forms an intake port and uses the first intake boat during low-speed operation and uses both the first and second intake ports during high-speed operation, the intake port of the first intake port is formed to have a larger diameter than the intake hole of the second intake boat, and the intake passage of the intake boat is connected to the vortex generation part at the end of the passage that communicates with the intake hole and surrounds the intake valve, and from the introduction part other than the end of this passage to Sakaki. The width of the valve stem layer 1 m of the intake valve of the first intake boat and the circumferential surface 1111 of the vortex generating part facing this is defined as the inner part of the cylinder chamber u1
Make it wider than the inside part and create a whirlpool! Connect the introduction part to the outside part of the valve, and adjust the height between the opening surface of the intake hole of the first intake port and the ceiling of the vortex generation part facing it from the wide outside part to the narrow one around the valve stem. The average reduction amount is determined by the diameter of the intake hole per 7 degrees around the valve stem.
A two-valve intake port for an internal combustion engine, characterized in that the intake port is set to 0% or more and 07g% or less.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58245762A JPS60142016A (en) | 1983-12-28 | 1983-12-28 | Two-valve intake port for internal combustion engines |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP58245762A JPS60142016A (en) | 1983-12-28 | 1983-12-28 | Two-valve intake port for internal combustion engines |
Publications (1)
| Publication Number | Publication Date |
|---|---|
| JPS60142016A true JPS60142016A (en) | 1985-07-27 |
Family
ID=17138419
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP58245762A Pending JPS60142016A (en) | 1983-12-28 | 1983-12-28 | Two-valve intake port for internal combustion engines |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS60142016A (en) |
-
1983
- 1983-12-28 JP JP58245762A patent/JPS60142016A/en active Pending
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