JP4131233B2 - Tappet guide - Google Patents

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JP4131233B2
JP4131233B2 JP2003419008A JP2003419008A JP4131233B2 JP 4131233 B2 JP4131233 B2 JP 4131233B2 JP 2003419008 A JP2003419008 A JP 2003419008A JP 2003419008 A JP2003419008 A JP 2003419008A JP 4131233 B2 JP4131233 B2 JP 4131233B2
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tappet
guide
cam
cylinder head
axial direction
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JP2005180229A (en
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貴文 重森
健 長谷川
剛 西田
紀行 田中
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Mitsubishi Motors Corp
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Mitsubishi Motors Corp
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/12—Transmitting gear between valve drive and valve
    • F01L1/14—Tappets; Push rods
    • F01L1/143—Tappets; Push rods for use with overhead camshafts
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01L—CYCLICALLY OPERATING VALVES FOR MACHINES OR ENGINES
    • F01L1/00—Valve-gear or valve arrangements, e.g. lift-valve gear
    • F01L1/46—Component parts, details, or accessories, not provided for in preceding subgroups

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)
  • Cylinder Crankcases Of Internal Combustion Engines (AREA)

Description

本発明は、とくに、エンジンのシリンダヘッドに形成され、カムにより駆動されてそれぞれ吸排気弁を往復動させるタペットを案内するためのタペットガイドに関する。   In particular, the present invention relates to a tappet guide for guiding a tappet formed on a cylinder head of an engine and driven by a cam to reciprocate an intake / exhaust valve.

従来のエンジンにおいては、図７に例示されているように、シリンダヘッド１に取り付けられたカム軸２の回転によりカム軸２のカム３が、コイルばね４のばね力に抗して略円筒状のタペットガイド５の軸方向にタペット６を直線的に往復動させることにより、吸気弁７または排気弁８を開閉作動させているが、タペットガイド５の上端面が回転するカム３と干渉しないように、タペットガイド５の軸方向において、タペットガイド５の上端面が図示するタペット６の上死点位置（タペット６がカム３のベース円と接している状態）より低く設定されているので、タペット６の上面上に十分のオイルを溜めることが難しいため、タペットガイド５の内周面とタペット６の外周面との間の全体的な潤滑を確保するのが容易でないという問題があった。   In the conventional engine, as illustrated in FIG. 7, the cam 3 of the cam shaft 2 is substantially cylindrical against the spring force of the coil spring 4 by the rotation of the cam shaft 2 attached to the cylinder head 1. The intake valve 7 or the exhaust valve 8 is opened and closed by linearly reciprocating the tappet 6 in the axial direction of the tappet guide 5, but the upper end surface of the tappet guide 5 does not interfere with the rotating cam 3. Further, in the axial direction of the tappet guide 5, the upper end surface of the tappet guide 5 is set lower than the top dead center position of the tappet 6 (in a state where the tappet 6 is in contact with the base circle of the cam 3). Since it is difficult to store sufficient oil on the upper surface of the tappet 6, there is a problem that it is not easy to ensure overall lubrication between the inner peripheral surface of the tappet guide 5 and the outer peripheral surface of the tappet 6. It was.

また、タペットガイド５の軸方向にタペット６を安定的に往復動させるためには、タペットガイド５の軸長を大きく確保することが有効であるので、図７に２点鎖線で示されているように下死点位置にあるタペット６の下端近傍までタペットガイド５を下方へ延ばすようにすると、タペットガイド５の下方でシリンダヘッド１に形成されるオイルジャケット９の高さを比較的小さくせざるをえず、このため、シリンダヘッド１の鋳造時にオイルジャケット９の空間を形成させるための中子が薄くなって、その中子の強度を確保することが難しかった。   Further, in order to stably reciprocate the tappet 6 in the axial direction of the tappet guide 5, it is effective to ensure a large axial length of the tappet guide 5, which is indicated by a two-dot chain line in FIG. 7. Thus, if the tappet guide 5 is extended downward to the vicinity of the lower end of the tappet 6 at the bottom dead center position, the height of the oil jacket 9 formed on the cylinder head 1 below the tappet guide 5 is relatively small. However, for this reason, the core for forming the space of the oil jacket 9 becomes thin when the cylinder head 1 is cast, and it is difficult to ensure the strength of the core.

一方、図８（Ａ）、（Ｂ）、（Ｃ）に順次それぞれ模式的に示されているように、カム軸２の回転に伴ってタペット６頂面の最外周部にカム３の山部が当接しているとき、タペットガイド５とタペット６との間に存在する隙間によりタペット６が傾いて、とくにタペット６の頂面周縁がカム軸２及びタペットガイド５の軸方向と直角にタペットガイド５の内周面へ当たり、タペットガイド５には局部的に大きな負荷が作用することとなるので、この負荷を支持するため図９に示されているように、タペットガイド５の周面と点火プラグホルダ１０の壁面とをリブ１１で連結して補強したものが知られている。
しかしながら、点火プラグホルダ１０の周辺は元々構造が複雑であるので、上記の場合には、シリンダヘッド１上面の構造が一層複雑化されることとなって、単に重量が増加するばかりでなく、各部の隙間を小さく形成せざるをえなくなる結果、シリンダヘッド１の鋳造時に各隙間空間を形成させるための中子が薄くなって、この面からも中子の強度を確保することが難しくなるという問題があった。 On the other hand, as schematically shown sequentially in FIGS. 8A, 8B, and 8C, the peak portion of the cam 3 is formed on the outermost peripheral portion of the top surface of the tappet 6 as the cam shaft 2 rotates. Is in contact with the tappet guide 5 and the tappet 6, the tappet 6 is inclined by the gap existing between the tappet guide 5 and the tappet 6. Since a large load is applied locally to the tappet guide 5 when it hits the inner peripheral surface of the tappet guide 5, as shown in FIG. What strengthened by connecting the wall surface of the plug holder 10 with the rib 11 is known.
However, since the structure around the spark plug holder 10 is originally complicated, in the above case, the structure of the upper surface of the cylinder head 1 is further complicated, and not only the weight is increased, but each part is also increased. As a result, the gaps for forming the gap spaces become thin when the cylinder head 1 is cast, and it becomes difficult to ensure the strength of the cores from this surface as well. was there.

特許第２８４１３０７号公報Japanese Patent No. 2841307 実公平８−８２８５号公報No. 8-8285

本発明は、回転するカム軸のカムがタペットガイドの上端面と干渉することなく、タペットの上面上にオイルを効果的に溜めることができるようにすると共に、タペットガイドの剛性を確保しようとするものである。   The present invention makes it possible to effectively store oil on the upper surface of the tappet without causing the cam of the rotating cam shaft to interfere with the upper end surface of the tappet guide, and to ensure the rigidity of the tappet guide. Is.

このため、本発明にかかるタペットガイドは、シリンダヘッドにおいて、吸気弁駆動用または排気弁駆動用のカム軸を回動自在に支持する軸受部と連続して、カム軸の中心線方向に軸受部を挟んで軸受部の両側にそれぞれ形成され、カム軸のカムにより直接駆動されるタペットをその軸方向に沿って直線的に案内し、かつ、上端面が上記軸方向でタペットの上死点位置よりも高く形成されると共に、上端面のうち、上記中心線方向と直交する方向の部分に下方への凹部が形成され、さらに、上記凹部が形成された部分の上部肉厚が下部肉厚より大きく形成されている。   For this reason, the tappet guide according to the present invention includes a bearing portion in the center line direction of the cam shaft that is continuous with the bearing portion that rotatably supports the cam shaft for driving the intake valve or the exhaust valve in the cylinder head. The tappet is formed on both sides of the bearing part across the shaft and directly driven by the cam of the camshaft, and linearly guides the tappet along its axial direction. A lower recess is formed in a portion of the upper end surface in a direction perpendicular to the center line direction, and the upper thickness of the portion where the recess is formed is lower than the lower thickness. Largely formed.

本発明にかかるタペットガイドは、その上端面がタペットの軸方向においてタペットの上死点位置よりも高く形成されているため、タペットの上面上にオイルを容易に溜めることが可能となるので、タペットガイドの内周面とタペットの外周面との間を常に良好に潤滑させることができ、しかも、上端面がタペットの軸方向においてタペットの上死点位置よりも高く形成されていても、上端面のうちカム軸の中心線方向と直交する方向の部分に下方への凹部が形成されているため、カム軸の回転に伴うカムの回転軌跡と上端面が干渉することを容易に回避できて、カムによるタペットの駆動に支障を来すことを防止することが可能となる。 また、カムによるタペットの駆動に際しタペットの傾きによる荷重をタペットガイドの上記凹部が形成された部分が受けることになるが、この部分ではタペットガイドの上部肉厚が下部肉厚より大きく形成されているため、タペットガイドには上記荷重を支持できる剛性を容易に確保できる結果、補強構造を別途設置する必要がなくなって、シリンダヘッドの重量増加を抑制できる長所がある。   Since the upper end surface of the tappet guide according to the present invention is formed higher than the top dead center position of the tappet in the axial direction of the tappet, oil can be easily stored on the upper surface of the tappet. Even if the gap between the inner peripheral surface of the guide and the outer peripheral surface of the tappet is always well lubricated, and the upper end surface is formed higher than the top dead center position of the tappet in the axial direction of the tappet, the upper end surface Since a downward recess is formed in a portion perpendicular to the centerline direction of the camshaft, it is possible to easily avoid interference between the rotation locus of the cam and the upper end surface accompanying the rotation of the camshaft, It becomes possible to prevent the tappet from being driven by the cam. Further, when the tappet is driven by the cam, a load due to the inclination of the tappet is received by the portion where the concave portion of the tappet guide is formed. In this portion, the upper wall thickness of the tappet guide is formed larger than the lower wall thickness. For this reason, the tappet guide can easily secure the rigidity capable of supporting the above-mentioned load. As a result, there is no need to separately install a reinforcing structure, and there is an advantage that an increase in the weight of the cylinder head can be suppressed.

以下、本発明の実施例について説明する。   Examples of the present invention will be described below.

図１〜図６において、吸気２弁及び排気２弁式４シリンダエンジンのシリンダヘッド２０には、上方側壁２１により囲まれた内底面２２から上方へ突出するように軸受部２３、２４が形成され、軸受部２３、２４と軸受部２３、２４にボルト止めされたキャップ２５、２６とによって、吸気弁駆動用カム軸２７及び排気弁駆動用カム軸２８が互いに平行でそれぞれ回動自在に取り付けられている。   1 to 6, bearing portions 23 and 24 are formed on a cylinder head 20 of an intake two-valve and exhaust two-valve four-cylinder engine so as to protrude upward from an inner bottom surface 22 surrounded by an upper side wall 21. The intake valve drive camshaft 27 and the exhaust valve drive camshaft 28 are attached to each other in a freely rotatable manner by the bearing portions 23 and 24 and the caps 25 and 26 bolted to the bearing portions 23 and 24, respectively. ing.

また、カム軸２７、２８の中心線方向に軸受部２３、２４を挟んで軸受部２３、２４の両側に、すなわち、各シリンダ毎に、それぞれ上方側壁２１及び軸受部２３、２４と連続して各一対の略円筒状タペットガイド２９、３０が一体形成されている。   The cam shafts 27 and 28 are continuously connected to the upper side wall 21 and the bearing portions 23 and 24 on both sides of the bearing portions 23 and 24 with the bearing portions 23 and 24 interposed therebetween, that is, for each cylinder. Each pair of substantially cylindrical tappet guides 29 and 30 is integrally formed.

各タペットガイド２９にはそれぞれタペット３１がその軸方向に摺動自在に嵌挿され、タペット３１はカム軸２７のカム３２によりコイルばね３３のばね力に抗し上記軸方向に沿いタペットガイド２９で直線的に案内されて往復動することにより、吸気弁３４を開閉作動させている。   A tappet 31 is fitted in each tappet guide 29 so as to be slidable in the axial direction. The tappet 31 is against the spring force of the coil spring 33 by the cam 32 of the cam shaft 27 and is moved along the axial direction by the tappet guide 29. The intake valve 34 is opened and closed by reciprocating while being guided linearly.

同様にして、各タペットガイド３０にはそれぞれタペット４１がその軸方向に摺動自在に嵌挿され、タペット４１はカム軸２８のカム４２によりコイルばね４３のばね力に抗し上記軸方向に沿いタペットガイド３０で直線的に案内されて往復動することにより、吸気弁４４を開閉作動させている。   Similarly, a tappet 41 is inserted into each tappet guide 30 so as to be slidable in the axial direction thereof. The tappet 41 is opposed to the spring force of the coil spring 43 by the cam 42 of the cam shaft 28 along the axial direction. The intake valve 44 is opened and closed by linearly guided by the tappet guide 30 and reciprocating.

また、各シリンダ毎に、排気２弁及び排気２弁の中心部でシリンダヘッド２０の内底面２２に上方へ突出するボス部５０が設けられ、筒状の点火プラグガイド５１の下端がボス部５０に固定されている。   Further, for each cylinder, a boss portion 50 protruding upward is provided on the inner bottom surface 22 of the cylinder head 20 at the center of the exhaust 2 valve and the exhaust 2 valve, and the lower end of the cylindrical spark plug guide 51 is the boss portion 50. It is fixed to.

タペットガイド２９、３０の各上端面６１、６２は、シリンダヘッド２０の上方側壁２１より一段低く、かつ、タペットガイド２９、３０の軸方向において、それぞれタペット３１、４１の上死点位置より高く設定されているが、上端面６１、６２のうち、カム軸２７、２８の中心線方向とそれぞれ直交する方向の部分（カム軸２７、２８間に挟まれた側の部分）に、それぞれ下方への切欠き（凹部）６３、６４が形成されていて、それぞれカム軸２７、２８の回転に伴うカム３２、４２の回転軌跡に上端面６１、６２が干渉しないように構成されている。   The upper end surfaces 61 and 62 of the tappet guides 29 and 30 are set one step lower than the upper side wall 21 of the cylinder head 20 and higher than the top dead center position of the tappets 31 and 41 in the axial direction of the tappet guides 29 and 30, respectively. However, in the upper end surfaces 61 and 62, the portions in the direction orthogonal to the center line direction of the cam shafts 27 and 28 (the portion sandwiched between the cam shafts 27 and 28) are respectively moved downward. Notches (recesses) 63 and 64 are formed so that the upper end surfaces 61 and 62 do not interfere with the rotation trajectories of the cams 32 and 42 accompanying the rotation of the cam shafts 27 and 28, respectively.

また、タペットガイド２９、３０の下端面６５、６６は、タペットガイド２９、３０の軸方向において、それぞれ回転するカム３２、４２がタペット３１、４１上面の最外周部に当接して、タペット３１、４１がカム３２、４２により押し下げ始められるときにおけるタペット３１、４１の下端部位置付近にくるように設定されていて、各上端面６１、６２がタペット３１、４１の上死点位置より高く設定されているため結果的に、下端面６５、６６とシリンダヘッド２０の内底面２２との間に比較的大きな間隔が形成されて、タペットガイド２９、３０の下方にはそれぞれ比較的大きい空間のオイルジャケット８０、８１が形成されている。   In addition, the lower end surfaces 65 and 66 of the tappet guides 29 and 30 are configured such that the rotating cams 32 and 42 in the axial direction of the tappet guides 29 and 30 abut against the outermost peripheral portion of the upper surface of the tappet 31 and 41, respectively. 41 is set to be near the lower end position of the tappets 31 and 41 when the cams 32 and 42 start to be pushed down, and the upper end surfaces 61 and 62 are set higher than the top dead center positions of the tappets 31 and 41. As a result, a relatively large space is formed between the lower end surfaces 65 and 66 and the inner bottom surface 22 of the cylinder head 20, and oil jackets having relatively large spaces are respectively provided below the tappet guides 29 and 30. 80 and 81 are formed.

さらに、図２及び図６に示されているように、タペットガイド２９、３０においてそれぞれ凹部６３、６４が形成された部分の上部６７、６８は、それらの下部よりも肉厚が大きく形成されている。   Further, as shown in FIGS. 2 and 6, the upper portions 67 and 68 of the portions where the concave portions 63 and 64 are formed in the tappet guides 29 and 30, respectively, are formed to be thicker than their lower portions. Yes.

また、各一対のタペットガイド２９、３０は、図４及び図５に示されているように、それぞれそれらの周壁の連接部分における下部６９、７０のみがシリンダヘッド２０と一体的に連結されていると共に、図１及び図２に示されているように、タペットガイド２９、３０の上記各連接部分が、カム軸２７、２８の直角方向における点火プラグガイドボス部５０の対角線位置で、それぞれ点火プラグガイドボス部５０と連続して一体形成されている。   Further, as shown in FIGS. 4 and 5, each of the pair of tappet guides 29 and 30 is integrally connected to the cylinder head 20 only at the lower portions 69 and 70 at the connecting portions of the peripheral walls. 1 and 2, the connecting portions of the tappet guides 29 and 30 are respectively positioned at diagonal positions of the spark plug guide boss portion 50 in the direction perpendicular to the cam shafts 27 and 28, respectively. The guide boss part 50 is integrally formed continuously.

すなわち、タペットガイド２９、３０の上端面６１、６２が、タペットガイド２９、３０の軸方向において、それぞれタペット３１、４１の上死点位置より高く設定されているため、タペット３１、４１、または、カム３２、４２に供給されたオイルを上端面６１、６２の内周側で容易に受け止めることができる等の作用により、タペット３１、４１の上面上にオイルを確実に溜めることが可能となるので、タペットガイド２９、３０の内周面とタペット３１、４１の外周面との間を常に良好に潤滑させて、タペット３１、４１のスムースな作動を確保することができる。   That is, since the upper end surfaces 61 and 62 of the tappet guides 29 and 30 are set higher than the top dead center position of the tappets 31 and 41 in the axial direction of the tappet guides 29 and 30, respectively, Since the oil supplied to the cams 32 and 42 can be easily received on the inner peripheral side of the upper end surfaces 61 and 62, the oil can be reliably accumulated on the upper surfaces of the tappets 31 and 41. The smooth movement of the tappets 31 and 41 can be ensured by always well lubricating between the inner peripheral surfaces of the tappet guides 29 and 30 and the outer peripheral surfaces of the tappets 31 and 41.

しかも、上記のように、タペットガイド２９、３０の上端面６１、６２が比較的高く設定されていても、上端面６１、６２にそれぞれ凹部６３、６４が形成されていて、それぞれカム軸２７、２８の回転に伴うカム３２、４２の回転軌跡に上端面６１、６２が干渉することを容易に回避できるので、カム３２、４２によるタペット３１、４１の駆動に支障を来すことを防止することが可能となる。   In addition, as described above, even if the upper end surfaces 61 and 62 of the tappet guides 29 and 30 are set to be relatively high, the upper end surfaces 61 and 62 are formed with recesses 63 and 64, respectively. Since it is possible to easily avoid the upper end surfaces 61 and 62 from interfering with the rotation locus of the cams 32 and 42 accompanying the rotation of the cam 28, it is possible to prevent the drive of the tappets 31 and 41 by the cams 32 and 42 from being hindered. Is possible.

また、タペットガイド２９、３０の上端面６１、６２にそれぞれ凹部６３、６４が形成されていても、その部分の上部６７、６８における肉厚が下部と比較して大きく形成され、凹部６３、６４が形成されていないタペットガイド２９、３０の他の部分と同等の断面積を確保することが容易にできることにより、簡単な構造でタペットガイド２９、３０の全周にわたって十分の剛性を付与することができると共に、凹部６３、６４が形成されていない上端面６１、６２の部分と凹部６３、６４との接続個所、及び、凹部６３、６４内の屈曲面個所がいずれも大きな屈曲半径で連続形成されていて、凹部６３、６４の形成による応力集中の発生を防止することができる。   Further, even if the upper end surfaces 61 and 62 of the tappet guides 29 and 30 are respectively formed with the recesses 63 and 64, the thicknesses of the upper portions 67 and 68 of the portions are larger than the lower portions, and the recesses 63 and 64 are formed. Since it is possible to easily ensure the same cross-sectional area as the other portions of the tappet guides 29, 30 where no tappet is formed, it is possible to provide sufficient rigidity over the entire circumference of the tappet guides 29, 30 with a simple structure. The upper end surfaces 61 and 62 where the concave portions 63 and 64 are not formed and the connecting portions between the concave portions 63 and 64 and the bent surface portions within the concave portions 63 and 64 are both continuously formed with a large bending radius. Therefore, the occurrence of stress concentration due to the formation of the recesses 63 and 64 can be prevented.

さらに、タペットガイド２９、３０の上端面６１、６２が比較的高く設定されていて、タペットガイド２９、３０の軸長をそれだけ大きく確保することができるため、タペットガイド２９、３０の軸方向において、タペット３１、４１がカム３２、４２により押し下げ始められるときにおけるタペット３１、４１の下端部位置付近にタペットガイド２９、３０の下端面６５、６６がくるように、タペットガイド２９、３０の下端面６５、６６を比較的高く設定することが許容されて、タペットガイド２９、３０の下方にはそれぞれシリンダヘッド内底面２２との間に比較的大きい空間のオイルジャケット８０、８１を形成することが可能となるので、シリンダヘッド２０の鋳造時にオイルジャケット８０、８１の空間を形成させるための中子を厚く形成して、中子の強度を確保することが容易となる利点がある。   Furthermore, since the upper end surfaces 61 and 62 of the tappet guides 29 and 30 are set to be relatively high and the axial length of the tappet guides 29 and 30 can be secured so much, in the axial direction of the tappet guides 29 and 30, The lower end surfaces 65 of the tappet guides 29 and 30 are arranged so that the lower end surfaces 65 and 66 of the tappet guides 29 and 30 come near the positions of the lower end portions of the tappets 31 and 41 when the tappets 31 and 41 are started to be pushed down by the cams 32 and 42. 66 is allowed to be set relatively high, and oil jackets 80 and 81 having relatively large spaces can be formed below the tappet guides 29 and 30 and the cylinder head inner bottom surface 22 respectively. Therefore, a core for forming a space for the oil jackets 80 and 81 when the cylinder head 20 is cast. And thick, there is an advantage that it is easy to ensure the strength of the core.

他方、タペットガイド２９、３０は、それぞれ軸受部２３、２４を挟んで軸受部２３、２４の両側に上方側壁２１及び軸受部２３、２４と連続して一体形成されていると共に、それぞれそれらの周壁の連接部分がカム軸２７、２８の直角方向における点火プラグガイドボス部５０の対角線位置で点火プラグガイドボス部５０と連続して一体形成されていて、タペットガイド２９、３０の剛性を容易に高めることができるため、タペットガイド２９、３０自体の軽量化を図ることが可能となる。   On the other hand, the tappet guides 29 and 30 are formed integrally with the upper side wall 21 and the bearing portions 23 and 24 on both sides of the bearing portions 23 and 24 with the bearing portions 23 and 24 interposed therebetween, and the peripheral walls thereof. Are connected to the spark plug guide boss portion 50 continuously at a diagonal position of the spark plug guide boss portion 50 in the direction perpendicular to the cam shafts 27 and 28, and the rigidity of the tappet guides 29 and 30 is easily increased. Therefore, the tappet guides 29 and 30 themselves can be reduced in weight.

また、各一対のタペットガイド２９、３０は、それぞれそれらの周壁の連接部分における下部６９、７０のみがシリンダヘッド２０と一体的に連結されていて、従来装置と比較すると、タペットガイド２９、３０を支持するための余肉部分がきわめて少なく、従って、シリンダヘッド２０の大幅な軽量化を図ることができる上に、元々構造が複雑である点火プラグガイド５１及びボス部５０周辺の複雑化を抑制して、各部間の隙間を比較的大きくできるため、シリンダヘッド２０の鋳造時に使用される中子を厚く形成できることにより、この面からも中子の強度を確保することが容易となる長所がある。   Further, each of the pair of tappet guides 29, 30 is integrally connected to the cylinder head 20 only at the lower portions 69, 70 at the connecting portions of the peripheral walls, and the tappet guides 29, 30 are compared with the conventional apparatus. Therefore, the cylinder head 20 can be significantly reduced in weight, and the structure around the spark plug guide 51 and the boss portion 50, which originally has a complicated structure, can be suppressed. In addition, since the gaps between the respective parts can be made relatively large, the core used when casting the cylinder head 20 can be formed thick, so that the strength of the core can be easily secured from this surface.

本発明の実施例における概略平面図。The schematic plan view in the Example of this invention. 図１のII−II矢視縦断面拡大図。The II-II arrow longitudinal cross-sectional enlarged view of FIG. 図１の III−III 矢視縦断面拡大図。The III-III arrow longitudinal cross-sectional enlarged view of FIG. 図３のIV−IV断面図。IV-IV sectional drawing of FIG. 図３のＶ−Ｖ断面図。VV sectional drawing of FIG. 図４及び図５のVI矢視拡大図。The VI arrow enlarged view of FIG.4 and FIG.5. 従来装置の要部縦断面図。The principal part longitudinal cross-sectional view of a conventional apparatus. 上記従来装置の作用説明図。The operation explanatory view of the above-mentioned conventional device. 従来装置の一部上面図。The partial top view of the conventional apparatus.

符号の説明Explanation of symbols

１ シリンダヘッド
２３、２４ 軸受部
２７、２８ カム軸
２９、３０ タペットガイド
３１、４１ タペット
３２、４２ カム
３４ 吸気弁
４４ 排気弁
５０ ボス部
５１ 点火プラグガイド
６１、６２ 上端面
６３、６４ 凹部
６５、６６ 下端面
６７、６８ 上部
６９、７０ 連接部分下部
８０、８１ オイルジャケット DESCRIPTION OF SYMBOLS 1 Cylinder head 23, 24 Bearing part 27, 28 Cam shaft 29, 30 Tappet guide 31, 41 Tappet 32, 42 Cam 34 Intake valve 44 Exhaust valve 50 Boss part 51 Spark plug guide 61, 62 Upper end surface 63, 64 Recessed part 65, 66 Lower end face 67, 68 Upper part 69, 70 Lower part of connecting part 80, 81 Oil jacket

Claims (3)

シリンダヘッドにおいて、吸気弁駆動用または排気弁駆動用のカム軸を回動自在に支持する軸受部と連続して、上記カム軸の中心線方向に上記軸受部を挟んで上記軸受部の両側にそれぞれ形成され、上記カム軸のカムにより直接駆動されるタペットをその軸方向に沿って直線的に案内し、かつ、上端面が上記軸方向で上記タペットの上死点位置よりも高く形成されると共に、上記上端面のうち、上記中心線方向と直交する方向の部分に下方への凹部が形成され、さらに、上記凹部が形成された部分の上部肉厚が下部肉厚より大きく形成されたタペットガイド。   In the cylinder head, continuous with the bearing portion that rotatably supports the cam shaft for driving the intake valve or the exhaust valve, on both sides of the bearing portion with the bearing portion in the center line direction of the cam shaft. The tappets that are respectively formed and are directly driven by the cam of the cam shaft are linearly guided along the axial direction, and the upper end surface is formed higher in the axial direction than the top dead center position of the tappet. In addition, a tappet in which a downward recess is formed in a portion of the upper end surface in a direction orthogonal to the center line direction, and the upper wall thickness of the portion where the recess is formed is larger than the lower wall thickness. guide. 請求項１において、下端面が、上記軸方向において、上記カムによる上記タペットのカムリフト開始時における上記タペットの下端面位置付近と一致するように形成されたタペットガイド。   The tappet guide according to claim 1, wherein a lower end surface of the tappet is aligned with a vicinity of a position of a lower end surface of the tappet at the start of cam lift of the tappet by the cam in the axial direction. 請求項１または請求項２において、上記軸受部を挟んで上記軸受部の両側にそれぞれ隣接して形成された周壁の連接部分の下部が、上記シリンダヘッドに設けられて点火プラグガイドが嵌挿されるボス部と連続的に一体形成されたタペットガイド。   The lower part of the connection part of the surrounding wall formed adjacently on both sides of the said bearing part on both sides of the said bearing part in Claim 1 or Claim 2 is provided in the said cylinder head, and an ignition plug guide is inserted. Tappet guide that is continuously formed integrally with the boss.
JP2003419008A 2003-12-17 2003-12-17 Tappet guide Expired - Lifetime JP4131233B2 (en)

Priority Applications (3)

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JP2003419008A JP4131233B2 (en) 2003-12-17 2003-12-17 Tappet guide
DE200410060910 DE102004060910B4 (en) 2003-12-17 2004-12-17 tappet guide
CNB2004101013838A CN100360766C (en) 2003-12-17 2004-12-17 Tappet guide

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JP2003419008A JP4131233B2 (en) 2003-12-17 2003-12-17 Tappet guide

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JP2005180229A JP2005180229A (en) 2005-07-07
JP4131233B2 true JP4131233B2 (en) 2008-08-13

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DE102013207573A1 (en) * 2013-04-25 2014-10-30 Mahle International Gmbh Bearing frame or cylinder head cover
DE102014216859B4 (en) 2014-08-25 2022-06-02 Adidas Ag Metallic, additively manufactured footwear components for athletic performance
CN106224116B (en) * 2016-10-12 2018-01-19 广西玉柴机器股份有限公司 A kind of air cylinder head structure with spectacle tappet hole
CN106894908B (en) * 2017-03-15 2021-04-09 上汽通用汽车有限公司 Engine cylinder block

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AT329323B (en) * 1972-11-06 1976-05-10 Denzel Kraftfahrzeug Wolfgang CYLINDER HEAD FOR COMBUSTION MACHINERY
DE8326935U1 (en) * 1983-09-20 1987-10-22 Dr.Ing.H.C. F. Porsche Ag, 7000 Stuttgart Cylinder head for a preferably multi-cylinder internal combustion engine
JP2537205B2 (en) * 1986-07-09 1996-09-25 本田技研工業株式会社 Valve train for internal combustion engine
AT404387B (en) * 1991-03-04 1998-11-25 Avl Verbrennungskraft Messtech Internal combustion engine having two inlet valves and one outlet valve per cylinder
JPH08158933A (en) * 1994-11-30 1996-06-18 Yamaha Motor Co Ltd Four-cycle engine
US5570669A (en) * 1995-12-04 1996-11-05 Chrysler Corporation Cylinder head for an overhead camshaft internal combustion engine
JPH10280914A (en) * 1997-04-01 1998-10-20 Suzuki Motor Corp Tappet guide hole structure of engine
JP4396024B2 (en) * 2000-03-13 2010-01-13 マツダ株式会社 Cylinder head structure
JP3803288B2 (en) * 2001-12-13 2006-08-02 トヨタ自動車株式会社 Variable valve mechanism

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DE102004060910B4 (en) 2014-10-16
CN1629455A (en) 2005-06-22
JP2005180229A (en) 2005-07-07
CN100360766C (en) 2008-01-09

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