JP5102796B2 - Engine valve gear - Google Patents
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- JP5102796B2 JP5102796B2 JP2009063932A JP2009063932A JP5102796B2 JP 5102796 B2 JP5102796 B2 JP 5102796B2 JP 2009063932 A JP2009063932 A JP 2009063932A JP 2009063932 A JP2009063932 A JP 2009063932A JP 5102796 B2 JP5102796 B2 JP 5102796B2
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Description
本発明は、エンジンの動弁装置に関し、詳しくは、バルブブリッジの姿勢を安定化させることができるエンジンの動弁装置に関するものである。 The present invention relates to a valve operating apparatus for an engine, and more particularly to an engine valve operating apparatus capable of stabilizing the posture of a valve bridge.
従来のエンジンの動弁装置として、本発明と同様、一対のバルブがバルブスプリングで閉弁方向に付勢され、両バルブの上端のバルブ入力端部にバルブブリッジの長手方向両端のブリッジ出力部が載って、バルブブリッジが一対の弁軸入力端部上に架設され、このバルブブリッジの長手方向中央部にバルブブリッジのブリッジ入力部が形成され、このブリッジ入力部の上面にロッカアームの先端のロッカアーム出力部が接当され、ロッカアーム出力部の下向き揺動により、バルブブリッジが下向きに押され、一対のバルブがバルブスプリングの付勢力に抗して開弁され、ロッカアーム出力部の上向揺動で、一対のバルブとバルブブリッジとがバルブスプリングの付勢力で上昇して、一対のバルブが閉弁され、バルブブリッジは昇降ガイド部による案内なしで昇降されるようになっているものがある(例えば、特許文献１参照)。 As a conventional engine valve operating device, as in the present invention, a pair of valves are urged in the valve closing direction by valve springs, and bridge output portions at both ends in the longitudinal direction of the valve bridge are connected to valve input ends at the upper ends of both valves. The valve bridge is installed on the pair of valve shaft input ends, and the bridge input portion of the valve bridge is formed at the longitudinal center of the valve bridge. The rocker arm output at the tip of the rocker arm is formed on the upper surface of the bridge input portion. The part is touched, the rocker arm output part swings downward, the valve bridge is pushed downward, the pair of valves are opened against the urging force of the valve spring, and the rocker arm output part swings upward, The pair of valves and the valve bridge are raised by the biasing force of the valve spring, the pair of valves are closed, and the valve bridge There is adapted to be raised and lowered without that guidance (e.g., see Patent Document 1).
この種の動弁装置では、バルブブリッジと昇降ガイド部との摺動抵抗が無い分、馬力ロスが低減される利点がある。
しかし、従来のエンジンの動弁装置では、バルブブリッジの重心が高い位置にあるため、問題がある。
This type of valve operating device has the advantage that horsepower loss is reduced by the absence of sliding resistance between the valve bridge and the lifting guide.
However, the conventional engine valve operating device has a problem because the center of gravity of the valve bridge is at a high position.
上記従来技術では、次の問題がある。
《問題》 バルブブリッジの姿勢が不安定になる。
バルブブリッジの重心が高い位置にあるため、バルブブリッジの姿勢が不安定になる。このため、エンジン運転中、バルブブリッジが幅方向に傾きやすく、ロッカアーム出力部がブリッジ入力部に片当たりし、これらが磨耗しやすい。また、ブリッジ出力部がバルブ入力部に片当たりし、これらが磨耗しやすい。また、バルブの開閉タイミングのずれや開度の過不足が起こり、出力が低下しやすい。
The above prior art has the following problems.
<Problem> The posture of the valve bridge becomes unstable.
Since the center of gravity of the valve bridge is at a high position, the posture of the valve bridge becomes unstable. For this reason, during engine operation, the valve bridge tends to incline in the width direction, the rocker arm output part hits the bridge input part, and these wear easily. In addition, the bridge output part comes into contact with the valve input part, and these are easily worn. In addition, the valve opening / closing timing is shifted and the opening degree is excessive or insufficient, and the output tends to decrease.
本発明は、上記問題点を解決することができるエンジンの動弁装置、すなわち、バルブブリッジの姿勢を安定化させることができるエンジンの動弁装置を提供することを課題とする。 It is an object of the present invention to provide an engine valve gear that can solve the above-described problems, that is, an engine valve gear that can stabilize the attitude of a valve bridge.
(請求項１に係る発明)
請求項１に係る発明の発明特定事項は、次の通りである。
図３(Ａ)に例示するように、一対のバルブ(１)(１)がバルブスプリング(２)(２)で閉弁方向に付勢され、両バルブ(１)(１)の上端のバルブ入力部(３)(３)にバルブブリッジ(４)の長手方向両端のブリッジ出力部(５)(５)が載って、バルブブリッジ(４)が一対のバルブ入力部(３)(３)上に架設され、このバルブブリッジ(４)の長手方向中央部にバルブブリッジ(４)のブリッジ入力部(６)が形成され、このブリッジ入力部(６)の上面(７)にロッカアーム(８)の先端のロッカアーム出力部(９)が接当され、ロッカアーム出力部(９)の下向き揺動により、バルブブリッジ(４)が下向きに押され、一対のバルブ(１)(１)がバルブスプリング(２)(２)の付勢力に抗して開弁され、ロッカアーム出力部(９)の上向き揺動により、一対のバルブ(１)(１)とバルブブリッジ(４)とがバルブスプリング(２)(２)の付勢力で上昇して、一対のバルブ(１)(１)が閉弁され、バルブブリッジ(４)は昇降ガイド部による案内なしで昇降されるようになっている、エンジンの動弁装置において、
図５、図６に例示するように、ブリッジ入力部(６)の上面(７)にオイル溜め溝(１０)が凹設され、
バルブブリッジ(４)のブリッジ入力部(６)の下方に錘部(１１)が垂設され、
バルブブリッジ(４)の素材に焼結合金が用いられ、錘部(１１)にはバルブブリッジ(４)よりも比重の大きい素材が用いられ、
バルブブリッジ(４)の素材に焼結合金が用いられ、錘部(１１)から上向きに延長部(１１ｂ)が導出され、この延長部(１１ｂ)でバルブブリッジ(４)の他の部分よりも耐磨耗性の高いブリッジ入力部(６)が形成されている、ことを特徴とするエンジンの動弁装置。
(Invention of Claim 1)
Invention specific matters of the invention according to
As illustrated in FIG. 3A, a pair of valves (1) and (1) are urged in the valve closing direction by valve springs (2) and (2), and the valves at the upper ends of both valves (1) and (1). The bridge output parts (5) and (5) at both ends in the longitudinal direction of the valve bridge (4) are mounted on the input parts (3) and (3), and the valve bridge (4) is mounted on the pair of valve input parts (3) and (3). The bridge input portion (6) of the valve bridge (4) is formed at the longitudinal center of the valve bridge (4), and the rocker arm (8) is formed on the upper surface (7) of the bridge input portion (6). The rocker arm output section (9) at the tip is brought into contact, and the rocker arm output section (9) swings downward to push the valve bridge (4) downward, and the pair of valves (1) and (1) are moved to the valve spring (2 ) The valve is opened against the urging force of (2), and the pair of valves (1) (1) and valve bridge (4) are valved by the upward swinging of the rocker arm output section (9). As a result of the urging force of the bush springs (2) and (2), the pair of valves (1) and (1) are closed, and the valve bridge (4) is lifted and lowered without guidance by the lifting guide section. In the engine valve operating device,
As illustrated in FIGS. 5 and 6 , an oil sump groove (10) is formed in the upper surface (7) of the bridge input portion (6) ,
A weight part (11) is suspended below the bridge input part (6) of the valve bridge (4),
A sintered alloy is used for the material of the valve bridge (4), and a material having a specific gravity greater than that of the valve bridge (4) is used for the weight portion (11).
A sintered alloy is used for the material of the valve bridge (4), and an extension (11b) is led upward from the weight (11). A valve operating device for an engine, wherein a bridge input portion (6) having high wear resistance is formed.
（請求項１に係る発明）
《効果》 バルブブリッジの姿勢を安定化させることができる。
図５、図６に例示するように、ブリッジ入力部(６)の上面(７)にオイル溜め溝(１０)が凹設されているので、オイル溜め溝(１０)が除肉されている分だけ、バルブブリッジ(４)の重心が下がり、バルブブリッジ(４)の姿勢を安定化させることができる。このため、エンジン運転中、バルブブリッジ(４)が幅方向に傾きにくく、ロッカアーム出力部(９)がブリッジ入力部(６)に片当たりする不具合が抑制され、これらの磨耗が抑制される。また、ブリッジ出力部(５)がバルブ入力部(３)に片当たりする不具合も抑制され、これらの磨耗が抑制される。また、バルブ(１)の開閉タイミングのずれや開度の過不足が起こる不具合も抑制され、これらに起因する出力の低下も抑制される。
(Invention according to Claim 1)
<Effect> The posture of the valve bridge can be stabilized.
As illustrated in FIGS. 5 and 6 , since the oil reservoir groove (10) is formed in the upper surface (7) of the bridge input portion (6), the oil reservoir groove (10) is thinned. Only the center of gravity of the valve bridge (4) is lowered, and the posture of the valve bridge (4) can be stabilized. For this reason, during engine operation, the valve bridge (4) is not easily tilted in the width direction, and the problem that the rocker arm output portion (9) hits the bridge input portion (6) is suppressed, and wear of these is suppressed. Moreover, the trouble that the bridge output part (5) hits the valve input part (3) is also suppressed, and these wears are suppressed. Moreover, the malfunction which the shift | offset | difference of the opening-and-closing timing of valve | bulb (1) and the excess and deficiency of an opening degree arises is also suppressed, and the fall of the output resulting from these is also suppressed.
《効果》ロッカアーム出力部とブリッジ入力部の磨耗抑制機能が高い。
図５、図６に例示するように、ブリッジ入力部(６)の上面(７)にオイル溜め溝(１０)が凹設されているので、オイル溜め溝(１０)に溜まったエンジンオイルが、ロッカアーム出力部(９)とブリッジ入力部(６)との摺動面に供給される。このため、ロッカアーム出力部(９)とブリッジ入力部(６)の磨耗抑制機能が高い。
<Effect> The wear suppression function of the rocker arm output part and the bridge input part is high.
As illustrated in FIGS. 5 and 6 , since the oil reservoir groove (10) is recessed in the upper surface (7) of the bridge input portion (6), the engine oil accumulated in the oil reservoir groove (10) It is supplied to the sliding surfaces of the rocker arm output section (9) and the bridge input section (6). For this reason, the wear suppression function of the rocker arm output part (9) and the bridge input part (6) is high.
《効果》 バルブブリッジの姿勢安定化機能が高い。
図５、図６に例示するように、バルブブリッジ(４)のブリッジ入力部(６)の下方に錘部(１１)が垂設されているので、バルブブリッジ(４)の重心を効率的に下げることができ、バルブブリッジ(４)の姿勢安定化機能が高い。
<Effect> The posture stabilization function of the valve bridge is high.
As illustrated in FIG. 5 and FIG. 6 , since the weight portion (11) is suspended below the bridge input portion (6) of the valve bridge (4), the center of gravity of the valve bridge (4) can be efficiently increased. The valve bridge (4) has a high posture stabilization function.
《効果》 バルブブリッジの姿勢安定化機能が高い。
図５、図６に例示するように、バルブブリッジ(４)の素材に焼結合金が用いられ、錘部(１１)にはバルブブリッジ(４)よりも比重の大きい素材が用いられているので、バルブブリッジ(４)の重心を効率的に下げることができ、バルブブリッジ(４)の姿勢安定化機能が高い。
<Effect> The posture stabilization function of the valve bridge is high.
As illustrated in FIGS. 5 and 6 , a sintered alloy is used for the material of the valve bridge (4), and a material having a higher specific gravity than the valve bridge (4) is used for the weight portion (11). The center of gravity of the valve bridge (4) can be lowered efficiently, and the posture stabilization function of the valve bridge (4) is high.
《効果》 ブリッジ入力部の磨耗抑制機能が高い。
図５、６に例示するように、バルブブリッジ(４)の素材に焼結合金が用いられ、この錘部(１１)から上向きに延長部(１１ｂ)が導出され、この延長部(１１ｂ)でバルブブリッジ(４)の他の部分よりも耐磨耗性の高いブリッジ入力部(６)が形成されているので、ブリッジ入力部(６)の磨耗抑制機能が高い。
<Effect> The wear suppression function of the bridge input section is high.
As illustrated in FIGS. 5 and 6, a sintered alloy is used for the material of the valve bridge (4), and an extension (11 b) is led upward from the weight (11), and the extension (11 b) Since the bridge input portion (6) having higher wear resistance than the other portions of the valve bridge (4) is formed, the wear suppression function of the bridge input portion (6) is high.
（請求項２に係る発明）
請求項１に係る発明の効果に加え、次の効果を奏する。
《効果》 バルブブリッジの姿勢安定化機能が高い。
図５、図６に例示するように、錘部(１１)はブリッジ出力部(５)(５)よりも低い位置まで垂設されているので、バルブブリッジ(４)の重心を効率的に下げることができ、バルブブリッジ(４)の姿勢安定化機能が高い。
(Invention according to Claim 2)
In addition to the effect of the invention according to
<Effect> The posture stabilization function of the valve bridge is high.
As illustrated in FIGS. 5 and 6, since the weight portion (11) is suspended to a position lower than the bridge output portions (5) and (5), the center of gravity of the valve bridge (4) is efficiently lowered. The posture stabilization function of the valve bridge (4) is high.
（請求項３に係る発明）(Invention according to claim 3)
請求項１または請求項２に係る発明の効果に加え、次の効果を奏する。In addition to the effect of the invention according to
《効果》 バルブブリッジの姿勢安定化機能が高い。<Effect> The posture stabilization function of valve bridge is high.
図６に例示するように、錘部(１１)の下部(１１ａ)が錘部(１１)の他の部分よりも径大にされているので、バルブブリッジ(４)の重心を効率的に下げることができ、バルブブリッジ(４)の姿勢安定化機能が高い。 As illustrated in FIG. 6, the lower portion (11a) of the weight portion (11) is larger in diameter than the other portions of the weight portion (11), so that the center of gravity of the valve bridge (4) is efficiently lowered. The posture stabilization function of the valve bridge (4) is high.
(請求項４)
請求項１から請求項３のいずれかに係る発明の効果に加え、次の効果を奏する。
《効果》 ブリッジ出力部とバルブ入力部との磨耗抑制機能が高い。
図２(Ａ)に例示するように、バルブスプリング(２)(２)のスプリングリテーナ(１６)上に溜まったエンジンオイル(１７)が、バルブ入力部(３)が内嵌されていないバルブ入力部嵌合凹部(１３)の空き空間(１８)を介して、ブリッジ出力部(５)とバルブ入力部(３)との接当箇所に進入するように、スプリングリテーナ(１６)を配置したので、ブリッジ出力部(５)とバルブ入力部(３)との磨耗抑制機能が高い。
(Claim 4)
In addition to the effects of the invention according to any one of
<Effect> The wear suppression function between the bridge output section and the valve input section is high.
As illustrated in FIG. 2 (A), the engine oil (17) accumulated on the spring retainer (16) of the valve springs (2) and (2) is not input into the valve input portion (3). The spring retainer (16) is arranged so as to enter the contact point between the bridge output part (5) and the valve input part (3) through the empty space (18) of the part fitting recess (13). The wear suppression function of the bridge output part (5) and the valve input part (3) is high.
《効果》 バルブ異仕様エンジン間で、バルブブリッジを兼用することができる。
図５，６(Ｃ)に例示するように、両ブリッジ出力部(５)(５)の下部にバルブ入力部嵌合凹部(１３)(１３)が設けられ、各バルブ入力部嵌合凹部(１３)の内周面が相互に連続する径大円弧状内周面(１４)と径小円弧状内周面(１５)で構成され、両径小円弧状内周面(１５)は連続する径大円弧状内周面(１４)よりもバルブブリッジ(４)の長手方向中央寄りに配置され、または、両径小円弧状内周面(１５)は連続する径大円弧状内周面(１４)よりもバルブブリッジ(４)の長手方向端部寄りに配置され、一対のバルブ入力部(３)(３)はその両方が、一対の径大円弧状内周面(１４)(１４)に沿って内嵌され、または、一対のバルブ入力部(３)(３)はその両方が、一対の径小円弧状内周面(１５)(１５)に沿って内嵌されるので、バルブ入力部(３)の径とバルブ離間距離(１９)(２０)が相違するバルブ異仕様エンジン間で、バルブブリッジ(４)を兼用することができる。
<Effect> A valve bridge can be shared between engines with different valve specifications.
As illustrated in FIGS. 5 and 6C , valve input portion fitting recesses (13) and (13) are provided below the bridge output portions (5) and (5), and each valve input portion fitting recess ( 13) is constituted by a large-diameter arcuate inner peripheral surface (14) and a small-diameter arcuate inner peripheral surface (15), and the both small-diameter inner peripheral surfaces (15) are continuous. It is arranged closer to the center in the longitudinal direction of the valve bridge (4) than the large-arc-shaped inner peripheral surface (14), or both small-arc-shaped inner peripheral surfaces (15) are continuous large-arc-shaped inner peripheral surfaces ( 14) is arranged closer to the longitudinal end of the valve bridge (4), and both of the pair of valve input portions (3) and (3) are a pair of large-diameter inner circumferential surfaces (14) and (14). Or both of the pair of valve input portions (3) and (3) are fitted along the pair of small arcuate inner peripheral surfaces (15) and (15). Input part (3) diameter and valve separation distance (1 ) (20) between dissimilar valve different specifications engine, can also serve a valve bridge (4).
《効果》 バルブブリッジが長手方向にも幅方向にもずれることなく位置決めされる。
図５，６(Ｃ)に例示するように、一対のバルブ入力部(３)(３)はその両方が、一対の径大円弧状内周面(１４)(１４)に沿って内嵌され、または、一対のバルブ入力部(３)(３)はその両方が、一対の径小円弧状内周面(１５)(１５)に沿って内嵌されるので、一対のバルブ入力部(３)(３)と一対の径大円弧状内周面(１４)(１４)との接当、または、一対のバルブ入力部(３)(３)と一対の径小円弧状内周面(１５)(１５)との接当により、バルブブリッジ(４)が長手方向にも幅方向にもずれることなく位置決めされる。
<Effect> The valve bridge is positioned without shifting in the longitudinal direction or the width direction.
As illustrated in FIGS. 5 and 6C , the pair of valve input portions (3) and (3) are both fitted along the pair of large-diameter inner circumferential surfaces (14) and (14). Alternatively, since both of the pair of valve input portions (3) and (3) are fitted along the pair of small-diameter inner peripheral surfaces (15) and (15), the pair of valve input portions (3 ) (3) and a pair of large-diameter inner peripheral surfaces (14), (14), or a pair of valve input portions (3) (3) and a pair of small-diameter inner peripheral surfaces (15 ) (15), the valve bridge (4) is positioned without shifting in either the longitudinal direction or the width direction.
本発明の実施の形態を図面に基づいて説明する。図１から図３は本発明の第１参考形態に係るエンジンの動弁装置を説明する図、図４−９は本発明の第２参考形態、第１実施形態、第２実施形態、第３−５参考形態に係るエンジンの動弁装置を説明する図である。各参考形態と各実施形態では、立形の多気筒ディーゼルエンジンの動弁装置について説明する。 Embodiments of the present invention will be described with reference to the drawings. Diagram illustrating a valve operating system for an engine according to a first referential embodiment of Figure 3 the present invention from FIG. 1, a second referential embodiment of Figure 4-9 the present invention, the first embodiment, second embodiment, third It is a figure explaining the valve operating apparatus of the engine which concerns on -5 reference form . In each reference embodiment and each embodiment, a valve operating device for a vertical multi-cylinder diesel engine will be described.
本発明の第１参考形態の概要は、次の通りである。
図３(Ａ)に示すように、シリンダブロック(図外)の上部にシリンダヘッド(２１)が取り付けられ、シリンダヘッド(２１)の上部にヘッドカバー(２２)が取り付けられている。シリンダヘッド(２１)内には吸気ポート(２３)と排気ポート(図外)とプッシュロッド挿通孔(２４)とが設けられている。吸気ポート(２３)には一対の吸気弁口(２５)(２５)が設けられ、この一対の吸気弁口(２５)(２５)を開閉する一対の吸気バルブ(１)(１)が配置されている。
シリンダヘッド(２１)の上部にはロッカアームブラケット(２６)が取り付けられ、このロッカアームブラケット(２６)に枢軸(２７)を介してロッカアーム(８)が揺動自在に取り付けられている。プッシュロッド挿通孔(２４)にはプッシュロッド(２８)が挿通されている。ロッカアームブラケット(２６)とロッカアーム(８)は、ヘッドカバー(２２)内に収容されている。
The outline of the first reference embodiment of the present invention is as follows.
As shown in FIG. 3A, a cylinder head (21) is attached to the upper part of a cylinder block (not shown), and a head cover (22) is attached to the upper part of the cylinder head (21). An intake port (23), an exhaust port (not shown), and a push rod insertion hole (24) are provided in the cylinder head (21). The intake port (23) is provided with a pair of intake valve ports (25) and (25), and a pair of intake valves (1) and (1) for opening and closing the pair of intake valve ports (25) and (25) are arranged. ing.
A rocker arm bracket (26) is attached to an upper portion of the cylinder head (21), and a rocker arm (8) is swingably attached to the rocker arm bracket (26) via a pivot (27). The push rod (28) is inserted through the push rod insertion hole (24). The rocker arm bracket (26) and the rocker arm (8) are accommodated in the head cover (22).
図３(Ａ)に示すように、一対の吸気バルブ(１)(１)は、動弁カム(図外)からタペット(図外)とプッシュロッド(２８)とロッカアーム(８)とバルブブリッジ(４)とを順に介して連動される。排気ポート(図外)の排気弁口(図外)は１つで、図３(Ｂ)に示すように、排気バルブ(２９)は動弁カム(図外)からタペット(図外)とプッシュロッド(図外)とロッカアーム(３０)とを介して連動される。図３(Ａ)に示すように、吸気バルブ(１)(１)のロッカアーム(８)の上部にあるオイル流出孔(３４)には、オイルパン(３１)のエンジンオイル(１７)が、オイルポンプ(３２)の圧送力で、オイルギャラリ(３３)と枢軸(２７)とを介して供給されている。排気バルブ(２９)のロッカアーム(３３)の上部にあるオイル流出孔(３５)にも同様にオイルパン(３１)のエンジンオイル(１７)が供給されている。 As shown in FIG. 3 (A), the pair of intake valves (1) (1) are connected to a valve cam (not shown) from a tappet (not shown), a push rod (28), a rocker arm (8), and a valve bridge ( 4) are linked in order. The exhaust port (not shown) has one exhaust valve port (not shown). As shown in FIG. 3 (B), the exhaust valve (29) is pushed from the valve cam (not shown) to the tappet (not shown). It is interlocked via a rod (not shown) and a rocker arm (30). As shown in FIG. 3 (A), the engine oil (17) of the oil pan (31) is inserted into the oil outflow hole (34) at the top of the rocker arm (8) of the intake valves (1) (1). It is supplied through the oil gallery (33) and the pivot (27) by the pumping force of the pump (32). Similarly, the engine oil (17) of the oil pan (31) is also supplied to the oil outflow hole (35) in the upper part of the rocker arm (33) of the exhaust valve (29).
吸気バルブの動弁装置の概要は、次の通りである。
図２(Ａ)に示すように、一対のバルブ(１)(１)がバルブスプリング(２)(２)で閉弁方向に付勢され、両バルブ(１)(１)の上端のバルブ入力部(３)(３)にバルブブリッジ(４)の長手方向両端のブリッジ出力部(５)(５)が載って、バルブブリッジ(４)が一対のバルブ入力部(３)(３)上に架設されている。
このバルブブリッジ(４)の長手方向中央部にバルブブリッジ(４)のブリッジ入力部(６)が形成され、このブリッジ入力部(６)の上面(７)にロッカアーム(８)の先端のロッカアーム出力部(９)が接当され、ロッカアーム出力部(９)の下向き揺動により、バルブブリッジ(４)が下向きに押され、一対のバルブ(１)(１)がバルブスプリング(２)(２)の付勢力に抗して開弁され、ロッカアーム出力部(９)の上向き揺動により、一対のバルブ(１)(１)とバルブブリッジ(４)とがバルブスプリング(２)(２)の付勢力で上昇して、一対のバルブ(１)(１)が閉弁される。
バルブブリッジ(４)は昇降ガイド部による案内なしで昇降されるようになっている。
The outline of the valve operating device of the intake valve is as follows.
As shown in FIG. 2 (A), a pair of valves (1) (1) is urged in the valve closing direction by valve springs (2) (2), and the valve inputs at the upper ends of both valves (1) (1). The bridge output parts (5) and (5) at both ends in the longitudinal direction of the valve bridge (4) are placed on the parts (3) and (3), and the valve bridge (4) is placed on the pair of valve input parts (3) and (3). It is erected.
A bridge input portion (6) of the valve bridge (4) is formed at the longitudinal center of the valve bridge (4), and the rocker arm output at the tip of the rocker arm (8) is formed on the upper surface (7) of the bridge input portion (6). Part (9) is contacted, and the rocker arm output part (9) is swung downward, the valve bridge (4) is pushed downward, and the pair of valves (1) (1) are valve springs (2) (2) The valve is opened against the urging force of the rocker, and the pair of valves (1), (1) and the valve bridge (4) are attached to the valve springs (2), (2) by the upward swing of the rocker arm output section (9). The pair of valves (1) and (1) are closed by the force.
The valve bridge (4) is raised and lowered without guidance by the raising and lowering guide part.
吸気バルブの動弁装置の工夫は、次の通りである。
図１(Ａ)(Ｂ)、図２(Ａ)に示すように、ブリッジ入力部(６)の上面(７)にオイル溜め溝(１０)が凹設されている。このため、オイル溜め溝(１０)が除肉されている分だけ、バルブブリッジ(４)の重心が下がり、バルブブリッジ(４)の姿勢を安定化させることができる。また、オイル溜め溝(１０)に溜まったエンジンオイルが、ロッカアーム出力部(９)とブリッジ入力部(６)との摺動面に供給される。
図１(Ａ)(Ｂ)に示すように、ブリッジ入力部(６)は円柱形に形成され、オイル溜め溝(１０)は、バルブブリッジ(４)の長手方向に沿う直線状に形成されている。
The device for the valve operating device of the intake valve is as follows.
As shown in FIGS. 1A and 1B and FIG. 2A, an oil reservoir groove (10) is formed in the upper surface (7) of the bridge input portion (6). For this reason, the center of gravity of the valve bridge (4) is lowered as much as the oil sump groove (10) is thinned, and the posture of the valve bridge (4) can be stabilized. The engine oil accumulated in the oil sump groove (10) is supplied to the sliding surfaces of the rocker arm output part (9) and the bridge input part (6).
As shown in FIGS. 1A and 1B, the bridge input portion (6) is formed in a cylindrical shape, and the oil sump groove (10) is formed in a straight line along the longitudinal direction of the valve bridge (4). Yes.
図１(Ｂ)に示すように、バルブブリッジ(４)のブリッジ入力部(６)の下方に錘部(１１)が垂設されている。また、錘部(１１)はブリッジ出力部(５)(５)よりも低い位置まで垂設されている、このため、バルブブリッジ(４)の重心を効率的に下げることができ、バルブブリッジ(４)の姿勢安定化機能が高い。錘部(１１)は、バルブブリッジ(４)のブリッジ入力部(６)の真下に配置されている。 As shown in FIG. 1 (B), a weight part (11) is suspended below the bridge input part (6) of the valve bridge (4). Further, the weight portion (11) is suspended to a position lower than the bridge output portions (5) and (5). Therefore, the center of gravity of the valve bridge (4) can be lowered efficiently, and the valve bridge ( 4) The posture stabilization function is high. The weight portion (11) is disposed directly below the bridge input portion (6) of the valve bridge (4).
バルブブリッジ(４)の素材に焼結合金が用いられ、錘部(１１)にはバルブブリッジ(４)よりも比重の大きい素材が用いられている。バルブブリッジ(４)の素材に用いられる焼結合金は、鉄系焼結合金(ＳＭＦ)で、錘部(１１)に用いられる素材は鋼である。錘部(１１)は円柱形で、上部がバルブブリッジ(４)に埋設されることにより、バルブブリッジ(４)に固定されている。
ブリッジ入力部(６)の素材中に工具鋼の粉末が含有されている。工具鋼にはハイスが用いられている。
A sintered alloy is used for the material of the valve bridge (4), and a material having a higher specific gravity than the valve bridge (4) is used for the weight portion (11). The sintered alloy used for the material of the valve bridge (4) is an iron-based sintered alloy (SMF), and the material used for the weight part (11) is steel. The weight part (11) has a cylindrical shape and is fixed to the valve bridge (4) by burying the upper part in the valve bridge (4).
Tool steel powder is contained in the material of the bridge input section (6). High speed steel is used for tool steel.
図１(Ｂ)(Ｃ)に示すように、両ブリッジ出力部(５)(５)の下部にバルブ入力部嵌合凹部(１３)(１３)が設けられ、各バルブ入力部嵌合凹部(１３)の内周面が相互に連続する径大円弧状内周面(１４)と径小円弧状内周面(１５)で構成され、両径小円弧状内周面(１５)は連続する径大円弧状内周面(１４)よりもバルブブリッジ(４)の長手方向中央寄りに配置され、図２(Ｂ)に示すように、一対のバルブ入力部(３)(３)はその両方が、一対の径大円弧状内周面(１４)(１４)に沿って内嵌されている。
そして、図２(Ａ)に示すように、バルブスプリング(２)(２)のスプリングリテーナ(１６)上に溜まったエンジンオイル(１７)が、バルブ入力部(３)が内嵌されていないバルブ入力部嵌合凹部(１３)の空き空間(１８)を介して、ブリッジ出力部(５)とバルブ入力部(３)との接当箇所に進入するように、スプリングリテーナ(１６)を配置してある。
As shown in FIGS. 1B and 1C, valve input portion fitting recesses (13) and (13) are provided below the bridge output portions (5) and (5), and each valve input portion fitting recess ( 13) is constituted by a large-diameter arcuate inner peripheral surface (14) and a small-diameter arcuate inner peripheral surface (15), and the both small-diameter inner peripheral surfaces (15) are continuous. It is arranged closer to the center in the longitudinal direction of the valve bridge (4) than the large-circular arc-shaped inner peripheral surface (14). As shown in FIG. 2 (B), the pair of valve input portions (3) and (3) are both Is fitted along the pair of large-diameter inner circumferential surfaces (14), (14).
As shown in FIG. 2 (A), the engine oil (17) accumulated on the spring retainer (16) of the valve springs (2) and (2) is not fitted into the valve input part (3). The spring retainer (16) is arranged so as to enter the contact point between the bridge output part (5) and the valve input part (3) through the empty space (18) of the input part fitting recess (13). It is.
この第１参考形態は、バルブ入力部(３)の径が大きく、長いバルブ離間距離(２０)の大径長離間バルブ仕様エンジンに関するものであるが、バルブ入力部(３)の径が小さく、短いバルブ離間距離(１９)の小径短離間仕様バルブエンジンでは、一対のバルブ入力部(３)(３)はその両方が、一対の径小円弧状内周面(１５)(１５)に沿って内嵌される。このため、大径長離間バルブ仕様エンジンと小径短離間仕様バルブエンジンとでバルブブリッジ(４)を兼用することができる。他の参考形態や実施形態でも同じである。 The first reference embodiment relates to a large-diameter long-separated valve engine having a large valve input portion (3) and a long valve separation distance (20), but the valve input portion (3) has a small diameter, In a small-diameter short-separation type valve engine with a short valve separation distance (19), both of the pair of valve input portions (3) and (3) are along a pair of small-diameter arcuate inner peripheral surfaces (15) and (15). It fits inside. For this reason, the large-diameter long-separation valve specification engine and the small-diameter short-separation specification valve engine can share the valve bridge (4). The same applies to other reference forms and embodiments.
この第１参考形態では、図１(Ｃ)に示すように、両径小円弧状内周面(１５)は連続する径大円弧状内周面(１４)よりもバルブブリッジ(４)の長手方向中央寄りに配置されているが、両径小円弧状内周面(１５)は連続する径大円弧状内周面(１４)よりもバルブブリッジ(４)の長手方向端部寄りに配置されるものであってもよい。この場合、バルブ入力部(３)の径が小さく、長いバルブ離間距離の小径長離間バルブ仕様エンジンと、バルブ入力部(３)の径が大きく、短いバルブ離間距離の大径短離間バルブ仕様エンジンとで、バルブブリッジ(４)を兼用することができる。他の参考形態や実施形態でも同じである。 In the first reference embodiment , as shown in FIG. 1C, the inner circumferential surface (15) having both small diameters is longer than the continuous large-arc-shaped inner circumferential surface (14). Although it is arranged closer to the center in the direction, the small-diameter inner peripheral surface (15) of both diameters is arranged closer to the longitudinal end of the valve bridge (4) than the continuous large-arc inner peripheral surface (14). It may be a thing. In this case, a small-diameter long-separated valve specification engine with a small valve input portion (3) and a long valve separation distance, and a large-diameter short-separation valve specification engine with a large valve input portion (3) and a short valve separation distance. Thus, the valve bridge (4) can also be used. The same applies to other reference forms and embodiments.
図４−９に示す第２参考形態、第１実施形態、第２実施形態、第３−５参考形態では、次の点を備えている。
図４に示す第２参考形態では、錘部(１１)の下部(１１ａ)が錘部(１１)の他の部分よりも径大にされている。この第２参考形態では、第１参考形態と同様、ブリッジ入力部(６)の素材中にも工具鋼の粉末が含有されている。
図５に示す第１実施形態では、バルブブリッジ(４)の素材に焼結合金が用いられ、錘部(１１)から上向きに延長部(１１ｂ)が導出され、この延長部(１１ｂ)でバルブブリッジ(４)の他の部分よりも耐磨耗性の高いブリッジ入力部(６)が形成されている。
錘部(１１)には低炭素鋼が用いられ、浸炭焼き入れ処理を施して、ブリッジ入力部(６)の表面硬度が高められている。このため、ブリッジ入力部(６)は、バルブブリッジ(４)の他の部分よりも硬度も密度も高く、耐摩耗性も高い。ブリッジ入力部(６)の表面硬度を高めるには、光輝焼き入れ処理を施してもよい。また、錘部(１１)に肌焼き鋼(低炭素鋼の一種)を用い、ブリッジ入力部(６)に高周波焼き入れ処理やレーザー焼き入れ処理等の表面熱処理を施してもよい。
図６に示す第２実施形態では、錘部(１１)の下部(１１ａ)が錘部(１１)の他の部分よりも径大にされ、バルブブリッジ(４)の素材に焼結合金が用いられ、錘部(１１)から上向きに延長部(１１ｂ)が導出され、この延長部(１１ｂ)でバルブブリッジ(４)よりも耐磨耗性の高いブリッジ入力部(６)が形成されている。
The second reference form, the first embodiment, the second embodiment, and the 3-5 reference form shown in FIG. 4-9 have the following points.
In the second reference form shown in FIG. 4, the lower part (11a) of the weight part (11) is made larger in diameter than other parts of the weight part (11). In this 2nd reference form , the powder of tool steel is contained also in the raw material of a bridge input part (6) like the 1st reference form .
In the first embodiment shown in FIG. 5, a sintered alloy is used for the material of the valve bridge (4), and the extension (11b) is led upward from the weight (11). The extension (11b) A bridge input portion (6) having higher wear resistance than other portions of the bridge (4) is formed.
Low carbon steel is used for the weight portion (11), and the surface hardness of the bridge input portion (6) is increased by carburizing and quenching. For this reason, the bridge input part (6) has higher hardness and density and higher wear resistance than the other parts of the valve bridge (4). In order to increase the surface hardness of the bridge input section (6), bright quenching treatment may be performed. Further, case-hardened steel (a kind of low carbon steel) may be used for the weight portion (11), and surface heat treatment such as induction hardening treatment or laser hardening treatment may be applied to the bridge input portion (6).
In the second embodiment shown in FIG. 6, the lower part (11a) of the weight part (11) is made larger in diameter than the other parts of the weight part (11), and a sintered alloy is used for the material of the valve bridge (4). The extension portion (11b) is led out upward from the weight portion (11), and the extension portion (11b) forms a bridge input portion (6) having higher wear resistance than the valve bridge (4). .
図７に示す第３参考形態では、第１参考形態と同様、バルブブリッジ(４)の素材に焼結合金が用いられ、ブリッジ入力部(６)の素材中に工具鋼の粉末が含有されている。この第５実施形態では、錘部(１１)も鉄系焼結合金(ＳＭＦ)である。
図８に示す第４参考形態では、第１参考形態と同様、バルブブリッジ(４)の素材には焼結合金が用いられ、錘部(１１)には焼結合金よりも比重の大きい鋼球(１２)が埋設されている。オイル溜め溝(１０)は、ブリッジ入力部(６)が円形になっている上面(７)の周縁部に沿って三日月形に形成され、バルブブリッジ(４)の一方の端部寄りに配置されている。この第４参考形態では、第１参考形態と同様、ブリッジ入力部(６)の素材中に工具鋼の粉末が含有されている。
図９に示す第５参考形態では、バルブブリッジ(４)の素材には焼結合金が用いられ、錘部(１１)には焼結合金よりも比重の大きい鋼球(１２)が埋設されている。バルブブリッジ(４)のブリッジ入力部(４)が円柱の幅方向両側を除肉して、除肉面(３６)(３６)が平坦面とされている。この第７実施形態では、第１参考形態と同様、ブリッジ入力部(６)の素材中に工具鋼の粉末が含有されている。
In the third reference form shown in FIG. 7, a sintered alloy is used for the material of the valve bridge (4), and the tool steel powder is contained in the material of the bridge input part (6), as in the first reference form. Yes. In the fifth embodiment, the weight portion (11) is also an iron-based sintered alloy (SMF).
In the fourth reference form shown in FIG. 8, a sintered alloy is used as the material of the valve bridge (4), and the weight (11) has a higher specific gravity than the sintered alloy, as in the first reference form. (12) is buried. The oil sump groove (10) is formed in a crescent shape along the peripheral edge of the upper surface (7) where the bridge input portion (6) is circular, and is disposed near one end of the valve bridge (4). ing. In the fourth reference form , as in the first reference form , tool steel powder is contained in the material of the bridge input section (6).
In the fifth reference embodiment shown in FIG. 9, a sintered alloy is used as the material of the valve bridge (4), and a steel ball (12) having a specific gravity larger than that of the sintered alloy is embedded in the weight portion (11). Yes. The bridge input part (4) of the valve bridge (4) is thinned on both sides in the width direction of the cylinder, and the thinning surfaces (36) and (36) are flat. In the seventh embodiment, as in the first reference embodiment , tool steel powder is contained in the material of the bridge input section (6).
図４−９に示す本発明の第２参考形態、第１実施形態、第２実施形態、第３−５参考形態は、上記で説明した以外の点は、第１参考形態と同じ構成と機能を備えている。図４−９中、第１参考形態と同一の要素には図１と同一の符号を付しておく。
尚、図１、４−７、９に示す第１参考形態、第２参考形態、第１実施形態、第２実施形態、第３参考形態、第５参考形態では、バルブブリッジ(４)は、バルブブリッジ(４)の長手方向の中央を幅方向に横断する直立平面に対して面対称の構造となる。
また、図８に示す第４参考形態では、バルブブリッジ(４)は、オイル溜め溝(１０)の部分を除き、同様の面対称の構造となる。
本発明は、上記各実施形態に限定されるものではなく、一対の排気バルブのバルブブリッジに用いてもよい。
The second reference form, the first embodiment, the second embodiment, and the 3-5 reference form of the present invention shown in FIG. 4-9 are the same in configuration and function as the first reference form except for the points described above. It has. 4-9, the same code | symbol as FIG. 1 is attached | subjected to the element same as 1st reference form .
In the first reference form, the second reference form, the first embodiment, the second embodiment, the third reference form, and the fifth reference form shown in FIGS. 1 , 4-7, and 9, the valve bridge (4) The valve bridge (4) has a plane-symmetric structure with respect to an upright plane that crosses the center in the longitudinal direction in the width direction.
Further, in the fourth reference embodiment shown in FIG. 8, the valve bridge (4) has the same plane-symmetric structure except the oil reservoir groove (10).
The present invention is not limited to the above embodiments, and may be used for a valve bridge of a pair of exhaust valves.
(１) バルブ
(２) バルブスプリング
(３) バルブ入力部
(４) バルブブリッジ
(５) ブリッジ出力部
(６) ブリッジ入力部
(７) 上面
(８) ロッカアーム
(９) ロッカアーム出力部
(１０) オイル溜め溝
(１１) 錘部
(１１ａ) 下部
(１１ａ) 延長部
(１２) 鋼球
(１３) バルブ入力部嵌合凹部
(１４) 径大円弧状内周面
(１５) 径小円弧状内周面
(１６) スプリングリテーナ
(１７) エンジンオイル
(１８) 空き空間
(１９) 短いバルブ離間距離
(２０) 長いバルブ離間距離
(1) Valve
(2) Valve spring
(3) Valve input section
(4) Valve bridge
(5) Bridge output section
(6) Bridge input section
(7) Top surface
(8) Rocker arm
(9) Rocker arm output section
(10) Oil reservoir groove
(11) Weight part
(11a) Lower part
(11a) Extension
(12) Steel balls
(13) Valve input part fitting recess
(14) Large-diameter arc-shaped inner peripheral surface
(15) Small circular arc inner peripheral surface
(16) Spring retainer
(17) Engine oil
(18) Free space
(19) Short valve separation distance
(20) Long valve separation distance
Claims (4)
ブリッジ入力部(６)の上面(７)にオイル溜め溝(１０)が凹設され、
バルブブリッジ(４)のブリッジ入力部(６)の下方に錘部(１１)が垂設され、
バルブブリッジ(４)の素材に焼結合金が用いられ、錘部(１１)にはバルブブリッジ(４)よりも比重の大きい素材が用いられ、
錘部(１１)から上向きに延長部(１１ｂ)が導出され、この延長部(１１ｂ)でバルブブリッジ(４)の他の部分よりも耐磨耗性の高いブリッジ入力部(６)が形成されている、ことを特徴とするエンジンの動弁装置。 A pair of valves (1) and (1) are energized in the valve closing direction by valve springs (2) and (2), and a valve bridge is connected to the valve input portions (3) and (3) at the upper ends of both valves (1) and (1). Bridge output portions (5) and (5) at both ends in the longitudinal direction of (4) are mounted, and the valve bridge (4) is installed on the pair of valve input portions (3) and (3). The bridge input part (6) of the valve bridge (4) is formed in the longitudinal center, and the rocker arm output part (9) at the tip of the rocker arm (8) is in contact with the upper surface (7) of the bridge input part (6). When the rocker arm output section (9) swings downward, the valve bridge (4) is pushed downward, and the pair of valves (1) (1) resists the urging force of the valve springs (2) (2). When the rocker arm output section (9) swings upward, the pair of valves (1) (1) and the valve bridge (4) urge the valve springs (2) (2). In rising, a pair of valves (1) (1) is closed, the valve bridge (4) is adapted to be raised and lowered without guidance by elevating guide portion, the valve gear of the engine,
An oil sump groove (10) is recessed in the upper surface (7) of the bridge input part (6) ,
A weight part (11) is suspended below the bridge input part (6) of the valve bridge (4) ,
A sintered alloy is used for the material of the valve bridge (4), and a material having a specific gravity greater than that of the valve bridge (4) is used for the weight portion (11) .
An extension portion (11b) is led upward from the weight portion (11), and the extension portion (11b) forms a bridge input portion (6) having higher wear resistance than other portions of the valve bridge (4). A valve operating device for an engine characterized by comprising:
錘部(１１)はブリッジ出力部(５)(５)よりも低い位置まで垂設されている、ことを特徴とするエンジンの動弁装置。 The valve operating apparatus for an engine according to claim 1 ,
The valve operating device for an engine, wherein the weight portion (11) is suspended to a position lower than the bridge output portions (5) and (5).
錘部(１１)の下部(１１ａ)が錘部(１１)の他の部分よりも径大にされている、ことを特徴とするエンジンの動弁装置。 The valve operating apparatus for an engine according to claim 1 or 2 ,
A valve operating device for an engine, characterized in that a lower portion (11a) of the weight portion (11) is made larger in diameter than other portions of the weight portion (11).
両ブリッジ出力部(５)(５)の下部にバルブ入力部嵌合凹部(１３)(１３)が設けられ、各バルブ入力部嵌合凹部(１３)の内周面が相互に連続する径大円弧状内周面(１４)と径小円弧状内周面(１５)で構成され、
両径小円弧状内周面(１５)は連続する径大円弧状内周面(１４)よりもバルブブリッジ(４)の長手方向中央寄りに配置され、または、両径小円弧状内周面(１５)は連続する径大円弧状内周面(１４)よりもバルブブリッジ(４)の長手方向端部寄りに配置され、
一対のバルブ入力部(３)(３)はその両方が、一対の径大円弧状内周面(１４)(１４)に沿って内嵌され、または、一対のバルブ入力部(３)(３)はその両方が、一対の径小円弧状内周面(１５)(１５)に沿って内嵌され、
バルブスプリング(２)(２)のスプリングリテーナ(１６)上に溜まったエンジンオイル(１７)が、バルブ入力部(３)が内嵌されていないバルブ入力部嵌合凹部(１３)の空き空間(１８)を介して、ブリッジ出力部(５)とバルブ入力部(３)との接当箇所に進入するように、スプリングリテーナ(１６)を配置した、ことを特徴とするエンジンの動弁装置。 The valve operating apparatus for an engine according to any one of claims 1 to 3 ,
Valve input portion fitting recesses (13) and (13) are provided at the lower portions of both bridge output portions (5) and (5), and the inner peripheral surfaces of the respective valve input portion fitting recesses (13) are large in diameter. An arc-shaped inner circumferential surface (14) and a small-diameter arc-shaped inner circumferential surface (15),
Both-diameter small arc-shaped inner peripheral surface (15) is arranged closer to the center in the longitudinal direction of the valve bridge (4) than the continuous large-diameter arc-shaped inner peripheral surface (14). (15) is disposed closer to the end in the longitudinal direction of the valve bridge (4) than the continuous large-diameter inner peripheral surface (14),
Both of the pair of valve input portions (3) and (3) are fitted along the pair of large-diameter inner circumferential surfaces (14) and (14), or the pair of valve input portions (3) and (3). ) Are both fitted along a pair of small arcuate inner circumferential surfaces (15), (15),
Engine oil (17) accumulated on the spring retainer (16) of the valve springs (2) and (2) is vacant in the valve input portion fitting recess (13) in which the valve input portion (3) is not fitted ( 18. A valve operating apparatus for an engine, characterized in that a spring retainer (16) is disposed so as to enter a contact portion between the bridge output section (5) and the valve input section (3) via 18).
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| Application Number | Priority Date | Filing Date | Title |
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| JP2009063932A JP5102796B2 (en) | 2008-09-16 | 2009-03-17 | Engine valve gear |
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| JP2008236131 | 2008-09-16 | ||
| JP2009063932A JP5102796B2 (en) | 2008-09-16 | 2009-03-17 | Engine valve gear |
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| JP2012215619A Division JP5444432B2 (en) | 2008-09-16 | 2012-09-28 | Engine valve gear |
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| JP2012215619A Expired - Fee Related JP5444432B2 (en) | 2008-09-16 | 2012-09-28 | Engine valve gear |
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| CN104712385B (en) * | 2015-03-27 | 2017-04-12 | 安徽江淮汽车集团股份有限公司 | Engine valve bridge structure |
| JP7124514B2 (en) * | 2018-07-25 | 2022-08-24 | 日産自動車株式会社 | Upper link in multi-link piston crank mechanism of internal combustion engine |
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| Publication number | Priority date | Publication date | Assignee | Title |
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| JPS53120651U (en) * | 1977-03-02 | 1978-09-26 | ||
| JPS5741363Y2 (en) * | 1978-10-11 | 1982-09-10 | ||
| JPS6436602U (en) * | 1987-08-31 | 1989-03-06 | ||
| JPH05248211A (en) * | 1992-03-04 | 1993-09-24 | Mitsubishi Motors Corp | Valve system for internal combustion engine |
| JP2000204914A (en) * | 1999-01-13 | 2000-07-25 | Mitsubishi Automob Eng Co Ltd | Valve system of internal combustion engine |
| JP2000310104A (en) * | 1999-04-28 | 2000-11-07 | Isuzu Motors Ltd | Valve system for engine |
| JP2001152816A (en) * | 1999-11-22 | 2001-06-05 | Yanmar Diesel Engine Co Ltd | Valve drive mechanism for engine |
| JP3780156B2 (en) * | 2000-08-11 | 2006-05-31 | 日野自動車株式会社 | Rocker arm |
| JPWO2003044333A1 (en) * | 2001-11-22 | 2005-03-24 | 日本精工株式会社 | Rocker arm |
| JP4003668B2 (en) * | 2003-03-06 | 2007-11-07 | 株式会社ジェイテクト | Rocker arm |
| JP2004293529A (en) * | 2003-03-28 | 2004-10-21 | Hino Motors Ltd | Valve gear of multi-valve engine |
| JP2005023830A (en) * | 2003-07-01 | 2005-01-27 | Sumitomo Electric Ind Ltd | Component having resistance to wear and slide |
| JP4233407B2 (en) * | 2003-07-17 | 2009-03-04 | 日野自動車株式会社 | Locker support installation structure |
| JP2007056822A (en) * | 2005-08-26 | 2007-03-08 | Kubota Corp | Multiple valve engine |
| JP2007138766A (en) * | 2005-11-16 | 2007-06-07 | Nissan Diesel Motor Co Ltd | Ohc type valve train of internal combustion engine |
| JP4540116B2 (en) * | 2006-02-13 | 2010-09-08 | Ｕｄトラックス株式会社 | Valve mechanism |
| JP5033742B2 (en) * | 2008-09-16 | 2012-09-26 | 株式会社クボタ | Engine valve gear |
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| JP2013019417A (en) | 2013-01-31 |
| JP5444432B2 (en) | 2014-03-19 |
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