JP2696249B2 - Intake device for internal combustion engine - Google Patents
Intake device for internal combustion engineInfo
- Publication number
- JP2696249B2 JP2696249B2 JP13277789A JP13277789A JP2696249B2 JP 2696249 B2 JP2696249 B2 JP 2696249B2 JP 13277789 A JP13277789 A JP 13277789A JP 13277789 A JP13277789 A JP 13277789A JP 2696249 B2 JP2696249 B2 JP 2696249B2
- Authority
- JP
- Japan
- Prior art keywords
- intake
- switching means
- speed
- switching
- low
- 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.)
- Expired - Lifetime
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- Valve Device For Special Equipments (AREA)
- Characterised By The Charging Evacuation (AREA)
Description
【発明の詳細な説明】 産業上の利用分野 本発明は、内燃機関の運転状態に応じて吸気弁の吸気
特性と吸気通路の吸気特性とを調整し、低速域から高速
域に亘り高い吸気特性を有する内燃機関の吸気装置に関
するものである。Description: BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention adjusts intake characteristics of an intake valve and intake characteristics of an intake passage in accordance with an operation state of an internal combustion engine, and achieves high intake characteristics from a low speed range to a high speed range. The present invention relates to an intake device for an internal combustion engine having:
従来技術 吸気弁の吸気特性を２種類の吸気特性に切換える可変
バルブタイミング切換手段を備え、かつ吸気通路を並列
に２列形成してその一方の吸気通路の上流側と下流端に
開閉弁を設けた３種類以上の吸気特性に切換えうる吸気
通路切換手段を備えた内燃機関は、特願昭63−92525号
に示されるように、従来から存在している。2. Description of the Related Art A variable valve timing switching means for switching the intake characteristic of an intake valve to two types of intake characteristics is provided. In addition, two rows of intake paths are formed in parallel, and open / close valves are provided at the upstream and downstream ends of one intake path. As shown in Japanese Patent Application No. 63-92525, an internal combustion engine provided with an intake passage switching means capable of switching to three or more types of intake characteristics has conventionally existed.
そして従来の前記内燃機関では、吸気通路の吸気特性
が３種類以上に切換え可能となっているため、吸気弁の
吸気特性の切換運転条件（例えば回転数）に対して吸気
通路の吸気特性の切換運転条件をずらせて、その吸気通
路の切換運転条件と吸気弁の切換運転条件とを組合せる
ことによって、４種類以上の吸気特性を得ることができ
る。In the conventional internal combustion engine, since the intake characteristics of the intake passage can be switched to three or more types, the intake characteristics of the intake passage are switched with respect to the operating condition (for example, the rotation speed) of the intake characteristics of the intake valve. By shifting the operating conditions and combining the switching operation condition of the intake passage and the switching operation condition of the intake valve, four or more types of intake characteristics can be obtained.
解決しようとする課題 しかし前記内燃機関においては、吸気通路を１気筒に
つき複数通路形成するとともに、その一方の吸気通路の
上、下流端に開閉弁をそれぞれ設けたため、構造が複雑
化してコストが高くなってしまう。However, in the internal combustion engine, a plurality of intake passages are formed for each cylinder, and on-off valves are provided at the upper and downstream ends of one of the intake passages. turn into.
課題を解決するための手段および作用効果 本発明はこのような難点を克服した内燃機関の吸気装
置の改良に係り、吸気弁の吸気特性を２種類の吸気特性
に切換える可変バルブタイミング切換手段と、吸気通路
の吸気特性を２種類の吸気特性に切換える吸気通路切換
手段とを備えた内燃機関であって、前記両切換手段のい
ずれか一方の切換手段は、或る運転状態を境にして相異
なる吸気特性に切換えられ、他方の切換手段は、前記一
方の切換手段の切換運転状態を含んだ運転状態の上、下
限を境にして一方、他方、一方の吸気特性に切換えられ
ることを特徴とするものである。Means for Solving the Problems and Effects The present invention relates to an improvement of an intake device for an internal combustion engine that overcomes such difficulties, and a variable valve timing switching means for switching intake characteristics of an intake valve between two types of intake characteristics. An internal combustion engine comprising: intake passage switching means for switching intake characteristics of an intake passage to two types of intake characteristics, wherein one of the two switching devices is different from each other with respect to a certain operating state. The air conditioner is switched to the intake characteristic, and the other switching means is switched to one or the other intake characteristic at the upper and lower limits of the operating state including the switching operation state of the one switching means. Things.
本発明は前記したように構成されているため、前記一
方の切換手段を一方の吸気特性に設定するとともに、前
記他方の切換手段を一方の吸気特性に設定することによ
って、第１の吸気特性状態で運転させることができる。Since the present invention is configured as described above, the first intake characteristic state is set by setting the one switching means to one intake characteristic and setting the other switching means to one intake characteristic. Can be driven.
次に前記一方の切換手段を一方の吸気特性に設定した
まま、前記他方の切換手段を一方の吸気特性から他方の
吸気特性に切換えることにより第２の吸気特性状態で運
転させることができる。また前記他方の切換手段を他方
の吸気特性に設定したまま、前記一方の切換手段を他方
の吸気特性に切換えることにより第３の吸気特性状態で
運転させることができる。さらに前記一方の切換手段を
他方の吸気特性に設定したまま、前記他方の切換手段を
一方の吸気特性に切換えることにより第４の吸気特性状
態で運転させることができる。Next, while the one switching means is set to the one intake characteristic, the other switching means is switched from the one intake characteristic to the other intake characteristic, whereby the operation can be performed in the second intake characteristic state. By switching the one switching means to the other intake characteristic while the other switching means is set to the other intake characteristic, it is possible to operate in the third intake characteristic state. Further, by switching the other switching means to the one intake characteristic while the one switching means is set to the other intake characteristic, it is possible to operate in the fourth intake characteristic state.
また本発明においては、可変バルブタイミング切換手
段および吸気通路切換手段をそれぞれ２種類の吸気特性
に切換えることができる構造とし、これらを組合せて４
種類の吸気特性に切換えることができるため、前記両切
換手段の構造をできるだけ単純化して、軽量化とコスト
ダウンを図ることができる。Further, in the present invention, the variable valve timing switching means and the intake passage switching means have a structure capable of switching to two kinds of intake characteristics, respectively,
Since it is possible to switch between different types of intake characteristics, the structure of the two switching means can be simplified as much as possible, and the weight and cost can be reduced.
さらに本発明では、前記可変バルブタイミング切換手
段および吸気通路切換手段の切換運転条件を相互にずら
せているため、一方の切換手段の切換運転状態における
吸気特性の低下を他方の切換手段による高水準の吸気特
性でもって補って、吸気特性を全運転域に亘り高い水準
に維持させることができる。Further, in the present invention, since the switching operation conditions of the variable valve timing switching means and the intake passage switching means are shifted from each other, the deterioration of the intake characteristic in the switching operation state of one switching means can be reduced to a high level by the other switching means. Supplemented by the intake characteristics, the intake characteristics can be maintained at a high level over the entire operating range.
実 施 例 以下図面に図示された本発明の一実施例について説明
する。Embodiment Hereinafter, an embodiment of the present invention illustrated in the drawings will be described.
自動車に搭載される図示の４サイクルエンジン１は、
直列４気筒４サイクルエンジンであり、シリンダブロッ
ク２の上端にシリンダヘッド３が一体に結合され、その
シリンダブロック２のシリンダ４にピストン５が摺動自
在に嵌装され、シリンダ４の頂部にはシリンダブロック
２とピストン５とで燃料室６が画成されている。The illustrated four-stroke engine 1 mounted on an automobile is:
An in-line four-cylinder four-cycle engine, in which a cylinder head 3 is integrally connected to an upper end of a cylinder block 2, a piston 5 is slidably fitted to a cylinder 4 of the cylinder block 2, and a cylinder The block 2 and the piston 5 define a fuel chamber 6.
またシリンダヘッド３には、それぞれ２対の吸気ポー
ト７、排気ポート８が形成されて、各吸気ポート７、排
気ポート８はそれぞれ吸気口９、排気口10を介して各燃
料室６に開口され、各吸気口９、排気口10にそれぞれ吸
気バルブ11、排気バルブ12が開閉自在に設けられてい
る。Further, two pairs of intake ports 7 and exhaust ports 8 are formed in the cylinder head 3, and each of the intake ports 7 and exhaust ports 8 is opened to each fuel chamber 6 through an intake port 9 and an exhaust port 10, respectively. An intake valve 11 and an exhaust valve 12 are provided at each of the intake port 9 and the exhaust port 10 so as to be freely opened and closed.
さらに吸気ポート７の上流側は各シリンダ４毎に１本
に集合されて、その上流端は吸気マニホールド13の吸気
通路14に接続され、吸気通路14の上流端はバイパス通路
15を介してエアクリーナ16に接続され、吸気通路14とバ
イパス通路15の接合部はエアクリーナ16の直下に位置し
て、吸気通路14とエアクリーナ16との連通を開閉自在に
遮断する吸気切換バルブ17が設けられており、エンジン
回転数NeがN1＜Ne＜N3の状態で吸気通路14とバイパス通
路15がとが連通され、N2の時に最大の出力トルクが得ら
れるように、吸気通路14、バイパス通路15の連通長の和
が設定され、エンジン回転数NeがN1より低い場合または
エンジン回転数NeがN3より高い場合に吸気切換バルブ17
が切換えられて、吸気通路14とエアクリーナ16とが連通
され、エンジン回転数NeがN3より高いN4の時に最大の出
力トルクが得られるように吸気通路14の通路長が設定さ
れている。Further, the upstream side of the intake port 7 is gathered into one for each cylinder 4, the upstream end of which is connected to the intake passage 14 of the intake manifold 13, and the upstream end of the intake passage 14 is a bypass passage
An intake switching valve 17 that is connected to the air cleaner 16 through the air passage 15 and that is located immediately below the air cleaner 16 at a junction between the intake passage 14 and the bypass passage 15 and that opens and closes the communication between the intake passage 14 and the air cleaner 16 in an openable and closable manner. The intake passage 14 and the bypass passage 15 are communicated with each other when the engine speed Ne is N 1 <Ne <N 3 , and the intake passage 14 is arranged so that the maximum output torque is obtained when the engine speed N is N 2. , is set the sum of the communication length of the bypass passage 15, the intake if when the engine speed Ne is less than N 1 or the engine rotational speed Ne is higher than N 3 switching valve 17
And is switched, the intake passage 14 and is passed through the air cleaner 16 are communicated, the engine speed Ne is set path length of the intake passage 14 so that the maximum output torque is obtained when the higher N 4 than N 3.
しかもシリンダヘッド３には、吸気バルブ11の頂端の
外方に位置してシリンダ４の配列方向に沿いロッカーシ
ャフト18が軸架され、この吸気バルブ11の頂端とロッカ
ーシャフト18との中間位置でこれと平行にカムシャフト
19が回転自在に枢支され、このカムシャフト19に低速カ
ム20、高速カム21、低速カム22が一体に設けられてい
る。In addition, a rocker shaft 18 is mounted on the cylinder head 3 outside the top end of the intake valve 11 along the direction in which the cylinders 4 are arranged, and a rocker shaft 18 is provided at an intermediate position between the top end of the intake valve 11 and the rocker shaft 18. Parallel to the camshaft
A low-speed cam 20, a high-speed cam 21, and a low-speed cam 22 are integrally provided on the camshaft 19.
またロッカーシャフト18には、低速ロッカーアーム2
3、高速ロッカーアーム24、低速ロッカーアーム25が回
転自在に嵌合されており、この低速ロッカーアーム23、
高速ロッカーアーム24、低速ロッカーアーム25はそれぞ
れ低速カム20、高速カム21、低速カム22に接触しうるよ
うになっている。The rocker shaft 18 has a low-speed rocker arm 2
3, the high-speed rocker arm 24 and the low-speed rocker arm 25 are rotatably fitted.
The high-speed rocker arm 24 and the low-speed rocker arm 25 can contact the low-speed cam 20, the high-speed cam 21, and the low-speed cam 22, respectively.
そして両側の低速ロッカーアーム23、低速ロッカーア
ーム25の先端にタペットねじ26が螺着され、このタペッ
トねじ26の下端に吸気バルブ11の頂端が当接し、中央の
高速ロッカーアーム24の先端下面に弾発付勢手段（図示
されず）が当接しており、バルブスプリング28および弾
発付勢手段のバネ力でもって低速ロッカーアーム23、高
速ロッカーアーム24、低速ロッカーアーム25が低速カム
20、高速カム21、低速カム22に圧接されるようになって
いる。A tappet screw 26 is screwed to the tip of the low-speed rocker arm 23 and the low-speed rocker arm 25 on both sides. The low-speed rocker arm 23, the high-speed rocker arm 24, and the low-speed rocker arm 25 are driven by the low-speed cam by the spring force of the valve spring 28 and the resilient urging device.
20, the high-speed cam 21 and the low-speed cam 22 are pressed against each other.
さらに高速ロッカーアーム24にはロッカーシャフト18
と平行な方向に指向して円筒状の貫通孔29が形成され、
低速カム20、高速カム21、低速カム22のベース円筒面に
低速ロッカーアーム23、高速ロッカーアーム24、低速ロ
ッカーアーム25が接触した位置関係にて、この貫通孔29
の両側延長線上で低速ロッカーアーム23、低速ロッカー
アーム25に油圧室30、ピン孔31が形成され、この貫通孔
29にこれと同じ長さの係止ピン32が摺動自在に嵌合され
るとともに、油圧室30、ピン孔31にそれぞれ、係止ピス
トン33、規制ピン34が摺動自在に嵌合され、ピン孔31の
底部と規制ピン34とに戻しスプリング35が介装され、ロ
ッカーシャフト18中に形成された圧力オイル通路36は連
通路37を介して油圧室30に連通されている。In addition, the high-speed rocker arm 24 has a rocker shaft 18
A cylindrical through hole 29 is formed in a direction parallel to
The through-hole 29 is formed in such a manner that the low-speed rocker arm 23, the high-speed rocker arm 24, and the low-speed rocker arm 25 are in contact with the base cylindrical surfaces of the low-speed cam 20, the high-speed cam 21, and the low-speed cam 22.
The hydraulic chamber 30 and the pin hole 31 are formed in the low-speed rocker arm 23 and the low-speed rocker arm 25 on the extension lines on both sides of the
A locking pin 32 of the same length is slidably fitted to 29, and a locking piston 33 and a regulating pin 34 are slidably fitted to the hydraulic chamber 30 and the pin hole 31, respectively. A return spring 35 is interposed between the bottom of the pin hole 31 and the regulating pin 34, and a pressure oil passage 36 formed in the rocker shaft 18 is communicated with the hydraulic chamber 30 via a communication passage 37.
そしてエンジン回転数NeがN2以下の場合では、圧力オ
イル通路36から図示されないオイルポンプに通ずる通路
に介装された切換バルブ（図示されず）が遮断状態とな
って、油圧室30に圧力オイルが供給されず、戻しスプリ
ング35のバネ力でもって係止ピストン33は油圧室30に押
込まれ、係止ピン32、係止ピストン33、規制ピン34相互
の各当接面が各低速ロッカーアーム23、高速ロッカーア
ーム24、低速ロッカーアーム25の隣接間隙に位置し、低
速ロッカーアーム23、高速ロッカーアーム24、低速ロッ
カーアーム25はそれぞれ別個に揺動でき、またエンジン
回転数NeがN2以上の場合では、前記切換バルブが開放状
態となって、圧力オイルが供給され、戻しスプリング35
のバネ力に打勝って係止ピストン33が貫通孔29に進入す
るとともに、係止ピン32がピン孔31に進入し、低速ロッ
カーアーム23、高速ロッカーアーム24、低速ロッカーア
ーム25が一体化されるようになっている。When the engine speed Ne is equal to or lower than N 2 , a switching valve (not shown) provided in a passage leading from the pressure oil passage 36 to an oil pump (not shown) is shut off, and the pressure oil is supplied to the hydraulic chamber 30. Is not supplied, the locking piston 33 is pushed into the hydraulic chamber 30 by the spring force of the return spring 35, and the respective contact surfaces of the locking pin 32, the locking piston 33, and the regulating pin 34 are moved to the respective low-speed rocker arms 23. , fast rocker arm 24, located adjacent the gap of the low-speed rocker arm 25, the slow rocker arm 23, high-speed rocker arm 24, the slow rocker arm 25 can be independently swung respectively, and if the engine speed Ne is N 2 or more In this state, the switching valve is opened, pressure oil is supplied, and the return spring 35
The locking piston 33 enters the through-hole 29 by overcoming the spring force of the above, and the locking pin 32 enters the pin hole 31, and the low-speed rocker arm 23, the high-speed rocker arm 24, and the low-speed rocker arm 25 are integrated. It has become so.
図示の実施例は前記したように構成されているので、
エンジン回転数NeがN1＜Ne＜N2の場合では油圧室30に圧
力オイルが存在せず、第４図に図示されるように、低速
ロッカーアーム23、高速ロッカーアーム24、低速ロッカ
ーアーム25がそれぞれ別個に揺動でき、低速ロッカーア
ーム23、低速ロッカーアーム25はそれぞれ低速カム20、
低速カム22でもって開弁期間が短くかつ弁揚程が低い状
態で吸気バルブ11が動作されるとともに、第１図に図示
されるように吸気切換バルブ17が設定されて、エアクリ
ーナ16より吸気口９に達する吸気通路長が長く形成さ
れ、吸気バルブ11の吸気特性および吸気通路の吸気特性
がそれぞれ低速回転域に適合した状態で４サイクルエン
ジン１は運転される。Since the illustrated embodiment is configured as described above,
When the engine speed Ne is N 1 <Ne <N 2 , there is no pressure oil in the hydraulic chamber 30, and as shown in FIG. 4, the low-speed rocker arm 23, the high-speed rocker arm 24, and the low-speed rocker arm 25 Can swing independently of each other, and the low-speed rocker arm 23 and the low-speed rocker arm 25
The intake valve 11 is operated in a state where the valve opening period is short and the valve lift is low by the low-speed cam 22, and the intake switching valve 17 is set as shown in FIG. Is formed, and the four-stroke engine 1 is operated with the intake characteristics of the intake valve 11 and the intake characteristics of the intake passage adapted to the low-speed rotation range, respectively.
またエンジン回転数NeがN2を越えると、油圧室30に圧
力オイルが供給されて、第５図に図示されるように、低
速ロッカーアーム23、高速ロッカーアーム24、低速ロッ
カーアーム25が一体化され、低速ロッカーアーム23、低
速ロッカーアーム25はカム山の巾が広くて高さが高い高
速カム21によって開弁期間が長くかつ弁揚程が高い状態
で動作され、吸気バルブ11の吸気特性がN2より高い回転
域に適した状態で４サイクルエンジン１は運転される。Further, when the engine rotational speed Ne exceeds N 2, is supplied pressure oil to the hydraulic chamber 30, as illustrated in FIG. 5, the low-speed rocker arm 23, high-speed rocker arm 24, the slow rocker arm 25 is integrally The low-speed rocker arm 23 and the low-speed rocker arm 25 are operated by the high-speed cam 21 having a wide cam ridge and a high height for a long valve opening period and a high valve lift. The four-stroke engine 1 is operated in a state suitable for a rotation range higher than two .
さらにエンジン回転数NeがN3を越えると、第２図に図
示されるように吸気切換バルブ17が設定されて、エアク
リーナ16より吸気口９に達する吸気通路長が短かく形成
され、吸気通路の吸気特性がN3より高い回転域に適した
状態で４サイクルエンジン１は運転される。Further the engine revolution speed Ne exceeds N 3, is set intake switching valve 17 as illustrated in FIG. 2 is an intake passage length to reach the intake port 9 through the air cleaner 16 is formed shorter, the intake passage inlet characteristic is a four-cycle engine 1 in a state suitable for high rotational range than N 3 is operated.
さらにエンジン回転数NeがN1以下の場合では、エアク
リーナ16より吸気口９に達する長い吸気通路長で最もト
ルクの高い回転状態より離れて第６図の破線の如くトル
クが大巾に低下する領域にて、逆にエアクリーナ16より
吸気口９に達する吸気通路長を短縮することによってト
ルクの低下を阻止し、高い出力特性を得ることができ
る。Furthermore if the engine rotational speed Ne is N 1 below, the area where the dashed as torque Figure 6 away from most torque high rotation state in the long intake passage length to reach the intake port 9 through the air cleaner 16 is reduced by a large margin On the contrary, by reducing the length of the intake passage reaching the intake port 9 from the air cleaner 16, a decrease in torque can be prevented, and high output characteristics can be obtained.
吸気バルブ11のバルブタイミング切換とエアクリーナ
16より吸気口９に達する吸気通路長切換とをずらせて組
合せることにより、第６図に図示するように、４サイク
ルエンジンの１のトルクの山を４山に分散して、隣接す
る山が交わる谷を浅くすることができるので、４サイク
ルエンジン１を高い出力特性が運転させることができ
る。Switching valve timing of intake valve 11 and air cleaner
By changing the combination of the intake passage length switching reaching the intake port 9 from the intake port 16 as shown in FIG. 6, the peak of one torque of the four-cycle engine is dispersed into four peaks, and Since the intersecting valleys can be made shallower, the four-cycle engine 1 can be operated with high output characteristics.
前記第１図ないし第６図に図示の実施例では、低速回
転域から高速回転域に亘って、吸気通路長を短、長、短
と切換えたが、これを第７図に図示するように、吸気通
路を、長細，短太，長細，短太と切換えてもよく、この
実施例では、特に低速回転域における吸気特性が良好で
ある。In the embodiment shown in FIGS. 1 to 6, the length of the intake passage is switched from short to long and short to long over a range from a low-speed rotation range to a high-speed rotation range, as shown in FIG. Alternatively, the intake passage may be switched between long and thin, short and long, thin and short, and in this embodiment, the intake characteristics are particularly good in the low-speed rotation range.
また前記第１図ないし第６図に図示の実施例では、低
速回転域から高速回転域に亘ってバルブタイミングを、
開弁期間が短くかつ弁揚程が低い状態および開弁期間が
長くかつ弁揚程が高い状態の２段に切換え、吸気通路長
を短、長、短の３段に切換えたが、第８図に図示するよ
うに、バルブタイミングを、弁揚程−開弁期間にて、低
−短，高−長，低−短，高−長の４段に切換え、吸気通
路を長−細，短−太の２段に切換えるようにしてもよ
く、あるいは、バルブタイミングを、弁揚程−開弁期間
にて、高−長，低−短，高−長の３段に切換えてもよ
い。In the embodiment shown in FIGS. 1 to 6, the valve timing is controlled from a low-speed rotation range to a high-speed rotation range.
FIG. 8 shows a state in which the valve opening period is short and the valve head is low, and a valve opening period is long and the valve head is high. As shown in the figure, the valve timing is switched between low-short, high-long, low-short, and high-long during the valve lift-valve opening period, and the intake passage is switched between long-thin and short-thick. The valve timing may be switched to two stages, or the valve timing may be switched to three stages of high-long, low-short, and high-long during the valve lift-valve opening period.
また、前記実施例のバルブタイミングは開弁期間−弁
揚程共に変更する実施例を示しているが各エンジンの要
求特性に応じ、開弁時期や閉弁時期だけを変更したり、
弁揚程のみ変更する場合もありうる。さらに吸気系にお
いても、長短のみの切換の他に吸気特性に影響する吸気
管断面積や共鳴吸気系における共鳴管長切換、共鳴ボリ
ューム切換．共鳴吸気系のキャンセル技術さらには分配
チャンバ容量切換等の吸気特性可変技術に代えても良
い。Further, the valve timing of the above embodiment shows an embodiment in which both the valve opening period and the valve lift are changed, but according to the required characteristics of each engine, only the valve opening timing and the valve closing timing are changed,
Only the valve lift may be changed. In addition, in the intake system, in addition to switching only the length, the intake pipe cross-sectional area affecting the intake characteristics, the resonance pipe length switching in the resonance intake system, and the resonance volume switching. A technique for canceling the resonance intake system and a technique for changing the intake characteristics such as switching the capacity of the distribution chamber may be used.
第１図および第２図は本発明に係る内燃期間の吸気装置
の一実施例を図示した縦断正面図で、第１図は、吸気切
換バルブが低速に適合するように切換えられた状態を示
し、第２図はこれが高速に適合するように切換えられた
状態を示し、第３図は吸気ロッカーアームの平面図、第
４図および第５図はその要部縦断平面図で、第４図はバ
ルブタイミング切換手段が低速に適合するように切換え
られた状態を示し、第５図はこれが高速に適合するよう
に切換えられた状態を示し、第６図は本実施例の特性
図、第７図および第８図はそれぞれ本発明のさらに他の
実施例の特性図である。 １……４サイクルエンジン、２……シリンダブロック、
３……シリンダヘッド、４……シリンダ、５……ピスト
ン、６……燃料室、７……吸気ポート、８……排気ポー
ト、９……吸気口、10……排気口、11……吸気バルブ、
12……排気バルブ、13……吸気マニホールド、14……吸
気通路、15……バイパス通路、16……エアクリーナ、17
……吸気切換バルブ、18……ロッカーシャフト、19……
カムシャフト、20……低速カム、21……高速カム、22…
…低速カム、23……低速ロッカーアーム、24……高速ロ
ッカーアーム24、25……低速ロッカーアーム、26……タ
ペットねじ、28……バルブスプリング、29……貫通孔、
30……油圧室、31……ピン孔、32……係止ピン、33……
係止ピストン、34……規制ピン、35……戻しスプリン
グ、36……圧力オイル通路、37……連通路。1 and 2 are longitudinal sectional front views showing an embodiment of an intake device during an internal combustion period according to the present invention, and FIG. 1 shows a state in which an intake switching valve is switched so as to be adapted to a low speed. , FIG. 2 shows a state in which it is switched so as to be adapted at a high speed, FIG. 3 is a plan view of the intake rocker arm, FIGS. 4 and 5 are longitudinal sectional plan views of essential parts thereof, and FIG. FIG. 5 shows a state in which the valve timing switching means has been switched to adapt to a low speed, FIG. 5 shows a state in which the valve timing switching means has been switched to adapt to a high speed, FIG. 6 shows a characteristic diagram of this embodiment, and FIG. FIG. 8 and FIG. 8 are characteristic diagrams of still another embodiment of the present invention. 1 ... 4 cycle engine, 2 ... cylinder block,
3 ... cylinder head, 4 ... cylinder, 5 ... piston, 6 ... fuel chamber, 7 ... intake port, 8 ... exhaust port, 9 ... intake port, 10 ... exhaust port, 11 ... intake valve,
12 ... exhaust valve, 13 ... intake manifold, 14 ... intake passage, 15 ... bypass passage, 16 ... air cleaner, 17
…… Intake switching valve, 18 …… Rocker shaft, 19 ……
Camshaft, 20… Low speed cam, 21… High speed cam, 22…
… Low-speed cam, 23… Low-speed rocker arm, 24… High-speed rocker arm 24, 25… Low-speed rocker arm, 26… Tappet screw, 28… Valve spring, 29… Through hole,
30 ... Hydraulic chamber, 31 ... Pin hole, 32 ... Locking pin, 33 ...
Locking piston, 34 ... regulating pin, 35 ... return spring, 36 ... pressure oil passage, 37 ... communication passage.
Claims (5)
吸気特性を２種類の吸気特性に切換える可変バルブタイ
ミング切換手段と、吸気通路の吸気特性を２種類の吸気
特性に切換える吸気通路切換手段とを備えた内燃機関で
あって、前記両切換手段のいずれか一方の切換手段は、
或る運転状態を境にして相異なる吸気特性に切換えら
れ、他方の切換手段は、前記一方の切換手段の切換運転
状態を含んだ運転状態の上、下限を境にして一方、他
方、一方の吸気特性に切換えられることを特徴とする内
燃機関の吸気装置。A variable valve timing switching means for switching the intake characteristic between two types of intake characteristics by changing an operation characteristic of the intake valve; and an intake passage switching means for switching the intake characteristic of the intake passage between two types of intake characteristics. An internal combustion engine provided with any one of the two switching means,
Switching to different intake characteristics is performed at a certain operating state, and the other switching means is one of the upper and lower operating states including the switching operation state of the one switching means, and the other is one of the other. An intake device for an internal combustion engine, which is switched to intake characteristics.
グ切換手段であって、前記他方の切換手段は吸気通路切
換手段であることを特徴とする前記特許請求の範囲第１
項記載の内燃機関の吸気装置。2. The apparatus according to claim 1, wherein said one switching means is a variable valve timing switching means, and said other switching means is an intake passage switching means.
An intake device for an internal combustion engine according to claim 1.
あって、前記他方の切換手段は可変バルブタイミング切
換手段であることを特徴とする内燃機関の吸気装置。3. An intake system for an internal combustion engine according to claim 1, wherein said one switching means is an intake passage switching means, and said other switching means is a variable valve timing switching means.
性は高速回転域に適合した吸気特性であることを特徴と
する前記特許請求の範囲第１項記載の内燃機関の吸気装
置。4. An intake system for an internal combustion engine according to claim 1, wherein one intake characteristic of said other switching means is an intake characteristic adapted to a high-speed rotation range.
性は低速回転域に適合した吸気特性であることを特徴と
する前記特許請求の範囲第１項記載の内燃機関の吸気装
置。5. An intake system for an internal combustion engine according to claim 1, wherein one intake characteristic of said other switching means is an intake characteristic adapted to a low-speed rotation range.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13277789A JP2696249B2 (en) | 1989-05-29 | 1989-05-29 | Intake device for internal combustion engine |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13277789A JP2696249B2 (en) | 1989-05-29 | 1989-05-29 | Intake device for internal combustion engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH03927A JPH03927A (en) | 1991-01-07 |
| JP2696249B2 true JP2696249B2 (en) | 1998-01-14 |
Family
ID=15089309
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13277789A Expired - Lifetime JP2696249B2 (en) | 1989-05-29 | 1989-05-29 | Intake device for internal combustion engine |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP2696249B2 (en) |
-
1989
- 1989-05-29 JP JP13277789A patent/JP2696249B2/en not_active Expired - Lifetime
Also Published As
| Publication number | Publication date |
|---|---|
| JPH03927A (en) | 1991-01-07 |
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