JP2009197732A - Valve train - Google Patents

Valve train Download PDF

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JP2009197732A
JP2009197732A JP2008041986A JP2008041986A JP2009197732A JP 2009197732 A JP2009197732 A JP 2009197732A JP 2008041986 A JP2008041986 A JP 2008041986A JP 2008041986 A JP2008041986 A JP 2008041986A JP 2009197732 A JP2009197732 A JP 2009197732A
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Prior art keywords
pair
rocker
valves
rocker shaft
rocker arm
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JP2008041986A
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JP5252946B2 (en
Inventor
Ken Sugiura
憲 杉浦
Shuichi Ezaki
修一 江▲崎▼
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Otics Corp
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Otics 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
    • F01L1/26—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder
    • F01L1/267—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of two or more valves operated simultaneously by same transmitting-gear; peculiar to machines or engines with more than two lift-valves per cylinder with means for varying the timing or the lift of the valves
    • 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
    • F01L1/18—Rocking arms or levers
    • F01L1/185—Overhead end-pivot rocking arms
    • 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
    • F01L1/20—Adjusting or compensating clearance
    • F01L1/22—Adjusting or compensating clearance automatically, e.g. mechanically
    • F01L1/24—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically
    • F01L1/2405—Adjusting or compensating clearance automatically, e.g. mechanically by fluid means, e.g. hydraulically by means of a hydraulic adjusting device located between the cylinder head and rocker arm
    • 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
    • F01L13/00—Modifications of valve-gear to facilitate reversing, braking, starting, changing compression ratio, or other specific operations
    • F01L13/0005—Deactivating valves
    • 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
    • F01L2305/00—Valve arrangements comprising rollers

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Valve-Gear Or Valve Arrangements (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To make a rocker arm to be hardly inclined in a width direction and to reduce variation of lift amounts among valves. <P>SOLUTION: A valve train 9 has a pair of lash adjuster 30a, 30b disposed at an interval, and is provided with a support hole 32 of a through-hole shape on a plunger 31 of each lash adjuster. A rocker shaft 40 is supported by the pair of lash adjusters 30a, 30b by inserting the rocker shaft 40 into the support holes 32, 32 of the pair of lash adjusters 30a, 30b. The rocker arm 20 driving a pair of valves 8, 8 of a same cylinder is rockably pivotally supported by the rocker shaft 40. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、内燃機関が回転するのに従いバルブを駆動する動弁機構に関する。   The present invention relates to a valve mechanism that drives a valve as an internal combustion engine rotates.

動弁機構の中には、図６に示す従来例（特許文献１）の動弁機構９０のように、同一シリンダ５（気筒）に対して設置された一対のバルブ８，８を駆動する一対のロッカアーム９２，９２を備え、各ロッカアーム９２が、上部半球型のラッシュアジャスタ９３の上に直接載置されて支持されたものがある。
特開２００６−１６１６５６号公報 Among the valve mechanisms, a pair of valves 8 and 8 for driving the same cylinder 5 (cylinder) as in the conventional valve mechanism 90 shown in FIG. There are rocker arms 92, 92, and each rocker arm 92 is directly mounted on and supported by an upper hemispherical lash adjuster 93.
JP 2006-161656 A

ところが、上記従来例では、各ロッカアーム９２が上部半球型のラッシュアジャスタ９３によって一点で支持されているため、該ロッカアーム９２がその幅方向に傾き易く、そのことが編摩耗等の原因となってしまうおそれがある。また、更に、該従来例では、一対のラッシュアジャスタ９３，９３が相互に独立しているため、該一対のラッシュアジャスタ９３，９３間でリークダウン量に違いが生じ、それによって、例えば、一対のロッカアーム９２，９２が一対のバルブ８，８をリフト量を揃えて開閉する設定になっている場合には、該リフト量が該一対のバルブ８，８間で相互にずれてしまい、また、例えば、一対のロッカアーム９２，９２が一対のバルブ８，８をバルブ間に所定のリフト量差をおいて開閉する設定になっている場合には、該所定のリフト量差がずれてしまい、燃費が悪化してしまうおそれがある。   However, in the above conventional example, each rocker arm 92 is supported at one point by the upper hemispherical lash adjuster 93, so that the rocker arm 92 is easily inclined in the width direction, which causes knitting wear and the like. There is a fear. Furthermore, in the conventional example, since the pair of lash adjusters 93 and 93 are independent of each other, a difference in the amount of leak-down occurs between the pair of lash adjusters 93 and 93, thereby, for example, a pair of lash adjusters 93 and 93. When the rocker arms 92 and 92 are set to open and close the pair of valves 8 and 8 with the same lift amount, the lift amounts deviate from each other between the pair of valves 8 and 8. When the pair of rocker arms 92 and 92 are set to open and close the pair of valves 8 and 8 with a predetermined lift amount difference between the valves, the predetermined lift amount difference is shifted and the fuel consumption is reduced. There is a risk of getting worse.

そこで、ロッカアームを幅方向へ傾き難くし、また、バルブ間でのリフト量のずれ、又はバルブ間に設定されている所定のリフト量差のずれ等を小さくすることを目的とする。   Accordingly, it is an object to make it difficult to tilt the rocker arm in the width direction, and to reduce a deviation in lift amount between valves or a difference in a predetermined difference in lift amount set between valves.

上記目的を達成するため、本発明の動弁機構は、一対のラッシュアジャスタが間隔をおいて設置され、該一対のラッシュアジャスタに一本のロッカシャフトが支持され、該一本のロッカシャフトに、同一気筒に対する複数のバルブを駆動する一又は複数のロッカアームが揺動可能に軸支されてなる。   In order to achieve the above object, in the valve operating mechanism of the present invention, a pair of lash adjusters are installed at intervals, and a single rocker shaft is supported by the pair of lash adjusters. One or a plurality of rocker arms for driving a plurality of valves for the same cylinder are pivotally supported.

ここで、前記一又は複数のロッカアームは、特に限定されないが、前記複数のバルブをリフト量を揃えて開閉する設定になっている場合や、前記複数のバルブをバルブ間に所定のリフト量差をおいて開閉する設定になってる場合が例として挙げられる。   Here, the one or the plurality of rocker arms are not particularly limited, but when the plurality of valves are set to open and close with the same lift amount, or when the plurality of valves have a predetermined lift amount difference between the valves. As an example, there is a case where it is set to open and close.

また、前記一本のロッカシャフトに軸支される前記ロッカアームの数及び形態は、特に限定されないが、次の（ア）（イ）の場合が例として挙げられる。
（ア）前記一本のロッカシャフトに、複数のバルブを駆動する一のロッカアームが軸支されている場合
（イ）前記一本のロッカシャフトに、各バルブをそれぞれ駆動する複数のロッカアームが軸支されている場合 Further, the number and form of the rocker arms that are pivotally supported by the single rocker shaft are not particularly limited, but the following cases (a) and (b) are given as examples.
(A) When one rocker arm that drives a plurality of valves is pivotally supported on the one rocker shaft (a) A plurality of rocker arms that respectively drive each valve are pivotally supported on the one rocker shaft. If

また、前記一対のラッシュアジャスタによる前記一本のロッカシャフトの支持は、特に限定されないが、次の（ウ）（エ）の場合が例として挙げられる。
（ウ）前記一対のラッシュアジャスタの各プランジャの上端部が半球状に形成され、一対の該プランジャの上端部の上に前記一本のロッカシャフトが載置されている場合
（エ）前記一対のラッシュアジャスタの各プランジャには貫通穴が設けられ、一対の該貫通穴に前記一本のロッカシャフトが挿入されている場合 Further, the support of the one rocker shaft by the pair of lash adjusters is not particularly limited, but the following cases (c) and (d) can be given as examples.
(C) The upper ends of the plungers of the pair of lash adjusters are formed in a hemispherical shape, and the one rocker shaft is placed on the upper ends of the pair of plungers. When each plunger of the lash adjuster is provided with a through hole, and the single rocker shaft is inserted into the pair of through holes

本発明によれば、ロッカアームが一本のロッカシャフトを介して一対のラッシュアジャスタに支持されるため、該ロッカアームは、幅方向へ傾き難くなる。また、該一対のラッシュアジャスタは該一本のロッカシャフトによって橋渡しされるため、両ラッシュアジャスタは連動し易く、よって、両ラッシュアジャスタ間にリークダウン量の違いが生じ難い。そのため、ロッカアームが複数のバルブをリフト量を揃えて開閉する設定になっている場合には、該リフト量がバルブ間でずれ難く、また、ロッカアームが複数のバルブをバルブ間に所定のリフト量差をおいて開閉する設定になっている場合には、該所定のリフト量差がずれ難い。   According to the present invention, since the rocker arm is supported by the pair of lash adjusters via the single rocker shaft, the rocker arm is difficult to tilt in the width direction. Further, since the pair of lash adjusters are bridged by the single rocker shaft, the two lash adjusters are easily interlocked, and therefore, a difference in the amount of leak-down is unlikely to occur between the two lash adjusters. Therefore, when the rocker arm is set to open and close multiple valves with the same lift amount, the lift amount is difficult to shift between the valves, and the rocker arm moves the multiple valves between the valves with a predetermined difference in lift amount. If it is set to open and close before the predetermined lift amount difference is difficult to shift.

本発明の動弁機構９は、一対のラッシュアジャスタ３０ａ，３０ｂが間隔をおいて設置され、各ラッシュアジャスタのプランジャ３１に貫通穴状の支持穴３２が設けられている。その一対のラッシュアジャスタ３０ａ，３０ｂの支持穴３２，３２に一本のロッカシャフト４０が挿入されることによって、該一対のラッシュアジャスタ３０ａ，３０ｂに該一本のロッカシャフト４０が支持されている。そして、該一本のロッカシャフト４０に、同一シリンダ５に対する一対のバルブ８，８を駆動するロッカアーム２０が揺動可能に軸支されている。   In the valve operating mechanism 9 of the present invention, a pair of lash adjusters 30a and 30b are installed at intervals, and a plunger 31 of each lash adjuster is provided with a support hole 32 having a through hole shape. The single rocker shaft 40 is supported by the pair of lash adjusters 30a and 30b by inserting the single rocker shaft 40 into the support holes 32 and 32 of the pair of lash adjusters 30a and 30b. A rocker arm 20 that drives a pair of valves 8 and 8 for the same cylinder 5 is pivotally supported on the single rocker shaft 40 so as to be swingable.

本実施例の図１〜図４に示す動弁機構９は、内燃機関の運転状況に応じてバルブの駆動状態を段階的に変更する可変式の動弁機構である。この動弁機構９は、本実施例では、複数あるシリンダ（気筒）のうちの半数のシリンダ５に対してのみ設置されており、各動弁機構９は、各シリンダ５に対して２本ずつ設けられた吸気用のバルブ８，８をリフト量を揃えて駆動する。この動弁機構９は、内燃機関の回転に従い回転する回転カム１０と、回転カム１０とバルブ８，８と間に揺動可能に介装され、バルブ８，８を開く方向へ付勢するロッカアーム２０と、バルブ８，８を閉じる方向へ付勢するバルブスプリング６０，６０と、ロッカアーム２０の状態を切り換える切換機構５０とを含み構成され、該ロッカアーム２０の状態を切り換えることにより、バルブ８，８を内燃機関の回転に従い駆動する駆動実行状態とその駆動を停止する駆動停止状態との間でバルブ８，８の駆動状態を変更する。   The valve operating mechanism 9 shown in FIGS. 1 to 4 of the present embodiment is a variable valve operating mechanism that changes the driving state of the valve stepwise in accordance with the operating state of the internal combustion engine. In this embodiment, the valve mechanisms 9 are installed only for half of the cylinders (cylinders), and two valve mechanisms 9 are provided for each cylinder 5. The provided intake valves 8, 8 are driven with the same lift amount. The valve mechanism 9 includes a rotary cam 10 that rotates in accordance with the rotation of the internal combustion engine, and a rocker arm that is swingably interposed between the rotary cam 10 and the valves 8 and 8 and biases the valves 8 and 8 in the opening direction. 20, valve springs 60, 60 that urge the valves 8, 8 in the closing direction, and a switching mechanism 50 that switches the state of the rocker arm 20. By switching the state of the rocker arm 20, the valves 8, 8 are configured. The drive state of the valves 8 and 8 is changed between a drive execution state in which the engine is driven according to the rotation of the internal combustion engine and a drive stop state in which the drive is stopped.

回転カム１０は、内燃機関が回転するのに従い回転駆動されるカムシャフト１０ｘに設けられており、基本部分となる断面形状が真円のベース円１１と、該ベース円１１から突出したカムノーズ１２とを含み構成されている。そして、この回転カム１０の外周面には、ロッカアーム２０に当接するカム面が形成されている。   The rotary cam 10 is provided on a camshaft 10x that is driven to rotate as the internal combustion engine rotates. The rotary cam 10 is a base circle 11 having a perfect cross-sectional shape as a basic part, and a cam nose 12 protruding from the base circle It is comprised including. A cam surface that contacts the rocker arm 20 is formed on the outer peripheral surface of the rotating cam 10.

ロッカアーム２０は、２つのバルブ８，８をリフト量を揃えて同時に駆動する２弁一体型のアームであって、回転カム１０に当接する入力部材２１と、バルブ８，８に当接する一対の出力部材２６ａ，２６ｂとからなり、一対のラッシュアジャスタ３０ａ，３０ｂに一本のロッカシャフト４０を介して揺動可能に支持されている。   The rocker arm 20 is a two-valve integrated arm that simultaneously drives the two valves 8 and 8 with the same lift amount. The rocker arm 20 has an input member 21 that contacts the rotating cam 10 and a pair of outputs that contact the valves 8 and 8. It consists of members 26a and 26b, and is supported by a pair of lash adjusters 30a and 30b via a single rocker shaft 40 so as to be swingable.

詳しくは、入力部材２１は、一対の出力部材２６ａ，２６ｂの相互間に設けられたインナアームであって、基端部に、ロッカシャフト４０に揺動可能に軸支されるための貫通穴状の支点穴２２を備え、先端部に、回転カム１０に回転可能に当接する入力ローラ２３を備えている。また、この入力部材２１とシリンダヘッド６との間には、該入力部材２１を回転カム１０に付勢するロストモーションスプリング２５が取り付けられている。   Specifically, the input member 21 is an inner arm provided between the pair of output members 26a and 26b, and has a through hole shape that is pivotally supported by the rocker shaft 40 at the base end portion. The fulcrum hole 22 is provided, and an input roller 23 that rotatably contacts the rotary cam 10 is provided at the tip. A lost motion spring 25 is attached between the input member 21 and the cylinder head 6 to urge the input member 21 toward the rotating cam 10.

また、一対の出力部材２６ａ，２６ｂは、入力部材２１の両側に設けられた、該入力部材２１よりも先端側に長いアウタアームであって、各出力部材は、基端部に、ロッカシャフト４０に揺動可能に軸支されるための貫通穴状の支点穴２７を備え、先端部に、バルブ８のステムエンド８ｅに当接する曲面状の出力面２８を備えている。   The pair of output members 26a and 26b are outer arms that are provided on both sides of the input member 21 and are longer on the distal end side than the input member 21, and each output member is connected to the rocker shaft 40 at the base end portion. A fulcrum hole 27 having a through hole for pivotally supporting the shaft 8 is provided, and a curved output surface 28 that abuts on the stem end 8e of the valve 8 is provided at the tip.

また、一対のラッシュアジャスタ３０ａ，３０ｂは、各プランジャ３１の上部に貫通穴状の支持穴３２を備えた上部リング型の油圧式のラッシュアジャスタであって、シリンダヘッド６に相互に間隔をおいて設置されている。各ラッシュアジャスタは、プランジャ３１が下降（リークダウン）した際には、ボディ３３の内部でプランジャ３１に押圧される高圧油室３４と、該高圧油室３４に逆止弁３６を介して連通し得る、プランジャ３１の内部に設けられた低圧油室３５と、プランジャ３１を上方へ押し返すスプリング３７とを備え、該プランジャ３１が下降した際には、高圧油室３４のオイルが、ボディ３３とプランジャ３１と間のクリアランスを経て低圧油室３５へリークする仕組みとなっている。この一対のラッシュアジャスタ３０ａ，３０ｂのプランジャ３１，３１の相互間に入力部材２１と一対の出力部材２６ａ，２６ｂとが配され、該一対のプランジャ３１，３１の支持穴３２，３２と該一対の出力部材２６ａ，２６ｂの支点穴２７，２７と該入力部材２１の支点穴２２とに、一本のロッカシャフト４０が挿通されることによって、該一対のプランジャ３１，３１に、該一本のロッカシャフト４０が支持されるとともに、該一本のロッカシャフト４０に、入力部材２１と一対の出力部材２６ａ，２６ｂとが揺動可能に軸支されている。   The pair of lash adjusters 30 a and 30 b are upper ring type hydraulic lash adjusters each having a through hole-like support hole 32 at the top of each plunger 31, and are spaced apart from each other by the cylinder head 6. is set up. Each lash adjuster communicates via a check valve 36 with a high pressure oil chamber 34 that is pressed by the plunger 31 inside the body 33 when the plunger 31 is lowered (leaked down). A low pressure oil chamber 35 provided inside the plunger 31 and a spring 37 that pushes back the plunger 31 upward, and when the plunger 31 is lowered, the oil in the high pressure oil chamber 34 The system leaks to the low-pressure oil chamber 35 via a clearance between The input member 21 and the pair of output members 26a and 26b are arranged between the plungers 31 and 31 of the pair of lash adjusters 30a and 30b, and the support holes 32 and 32 of the pair of plungers 31 and 31 and the pair of paired lash adjusters 30a and 30b. A single rocker shaft 40 is inserted into the fulcrum holes 27, 27 of the output members 26 a, 26 b and the fulcrum hole 22 of the input member 21, so that the pair of plungers 31, 31 has the single rocker. The shaft 40 is supported, and the input member 21 and the pair of output members 26a and 26b are pivotally supported on the single rocker shaft 40 so as to be swingable.

そのロッカシャフト４０に対しては、該ロッカシャフト４０をプランジャ３１に固定するシャフト固定部４１と、ロッカアーム２０の該ロッカシャフト４０に対する該シャフトの周方向への相対変位を許容しつつも、該ロッカアーム２０を該ロッカシャフト４０に該シャフトの長さ方向へ相対変位不能に係止するアーム係止部４６とが設けられている。詳しくは、シャフト固定部４１は、一方のラッシュアジャスタ３０ａとロッカシャフト４０との間にのみ設けられており、他方のラッシュアジャスタ３０ｂとロッカシャフト４０との間には設けられていない。このシャフト固定部４１は、該一方のラッシュアジャスタ３０ａの上端から支持穴３２に貫通する形で設けられた挿通穴４３と、該挿通穴４３に連通するようにロッカシャフト４０に設けられた雌ねじ状の螺刻穴４４と、該一方のラッシュアジャスタ３０ａの上方から挿通穴４３を挿通して螺刻穴４４に螺合したボルト４２とを含み構成されている。また、アーム係止部４６は、ロッカシャフト４０の外周部におけるロッカアーム２０の両側方に位置する部分に該外周部に沿って環状に凹設された取付溝４８，４８に、ロッカシャフト４０の側面に当接するＣリング４７，４７が取り付けられることによって構成されている。   The rocker shaft 40 has a shaft fixing portion 41 for fixing the rocker shaft 40 to the plunger 31 and the rocker arm 20 while allowing relative displacement of the rocker arm 20 relative to the rocker shaft 40 in the circumferential direction of the shaft. An arm locking portion 46 for locking 20 to the rocker shaft 40 so as not to be relatively displaced in the length direction of the shaft is provided. Specifically, the shaft fixing portion 41 is provided only between one lash adjuster 30 a and the rocker shaft 40, and is not provided between the other lash adjuster 30 b and the rocker shaft 40. The shaft fixing portion 41 has an insertion hole 43 provided so as to penetrate the support hole 32 from the upper end of the one lash adjuster 30a, and a female screw shape provided on the rocker shaft 40 so as to communicate with the insertion hole 43. And a bolt 42 inserted through the insertion hole 43 from above the one lash adjuster 30a and screwed into the screw hole 44. In addition, the arm locking portion 46 is provided in a side surface of the rocker shaft 40 in mounting grooves 48 and 48 that are annularly recessed along the outer peripheral portion of the rocker shaft 40 at portions located on both sides of the rocker arm 20. It is comprised by attaching C-rings 47 and 47 which contact | abut.

切換機構５０は、入力部材２１と出力部材２６ａ，２６ｂとを相互に相対揺動不能に連結した連結状態とその連結を解除した非連結状態との間で切換を行う機構であって、動弁機構９は、該切換により前述の駆動実行状態と駆動停止状態との間でバルブ８，８の駆動状態を変更する。この切換機構５０は、ロッカアーム２０の内部に、入力部材２１と出力部材２６ａ，２６ｂとの相互間を跨ぐ位置と跨がない位置との間で変位可能に取り付けられた連結ピン５１ａ，５１ｂと、該連結ピン５１ａ，５１ｂを油圧で一方向へ付勢する油圧機構５２と、該連結ピン５１ａ，５１ｂを復元力で前述の一方向とは反対側の他方向へ付勢するスプリング５６とを含み構成されている。詳しくは、この切換機構５０は、図４（ａ）に示すように、油圧機構５２の油圧で連結ピン５１ａ，５１ｂを一方向へ駆動することによって、非連結状態とし、図４（ｂ）に示すように、該油圧を緩めスプリング５６の復元力で連結ピン５１ａ，５１ｂを他方向へ駆動することによって、連結状態とする。   The switching mechanism 50 is a mechanism for switching between a connected state in which the input member 21 and the output members 26a and 26b are connected to each other so as not to be able to swing relative to each other and a disconnected state in which the connection is released. The mechanism 9 changes the drive state of the valves 8 and 8 between the drive execution state and the drive stop state by the switching. The switching mechanism 50 includes connecting pins 51a and 51b attached to the inside of the rocker arm 20 so as to be displaceable between a position straddling the input member 21 and the output members 26a and 26b and a position not straddling each other. A hydraulic mechanism 52 that urges the connecting pins 51a and 51b in one direction with hydraulic pressure, and a spring 56 that urges the connecting pins 51a and 51b in the other direction opposite to the one direction with a restoring force. It is configured. Specifically, as shown in FIG. 4 (a), the switching mechanism 50 is brought into a non-connected state by driving the connecting pins 51a and 51b in one direction with the hydraulic pressure of the hydraulic mechanism 52, as shown in FIG. 4 (b). As shown in the figure, the hydraulic pressure is loosened and the connecting pins 51a and 51b are driven in the other direction by the restoring force of the spring 56, thereby establishing a connected state.

連結ピン５１ａ，５１ｂは、入力ローラ２３の軸線上にて軸線方向へ変位可能に設けられており、一方の出力部材２６ａと入力部材２１との相互間を跨ぐ位置と跨がない位置との間で変位可能に設けられた第一連結ピン５１ａと、入力部材２１と他方の出力部材２６ｂとの相互間を跨ぐ位置と跨がない位置との間で変位可能に設けられた第二連結ピン５１ｂとを含み構成されている。なお、第二連結ピン５１ｂは、入力ローラ２３の軸穴を挿通することによって、該入力ローラ２３をベアリング２４を介して軸支している。それにより、入力ローラ２３を軸支するローラシャフトを別途設ける必要性が省かれ、入力部材２１の構造が簡素化されている。   The connecting pins 51a and 51b are provided so as to be displaceable in the axial direction on the axis of the input roller 23, and between the position between the one output member 26a and the input member 21 and the position not straddling. The second connecting pin 51b provided to be displaceable between the first connecting pin 51a provided so as to be displaceable and the position between the input member 21 and the other output member 26b and the position where the input member 21 does not straddle. And is configured. The second connecting pin 51 b pivotally supports the input roller 23 via the bearing 24 by inserting the shaft hole of the input roller 23. This eliminates the need to separately provide a roller shaft that pivotally supports the input roller 23, and the structure of the input member 21 is simplified.

油圧機構５２は、連結ピン５１ａ，５１ｂを油圧で駆動する、他方の出力部材２６ｂの内部に設けられた油圧室５３と、該油圧室５３と第二連結ピン５１ｂとの間に介装された、油圧室５３を閉塞する油圧ピン５４と、シリンダヘッド６、他方のラッシュアジャスタ３０ｂ、ロッカシャフト４０及び他方の出力部材２６ｂの内部を経由して設けられた、油圧室５３に油圧を供給する油路５５とを含み構成されている。そのため、油路５５は、シリンダヘッド６側の油路（図示略）と、他方のラッシュアジャスタ３０ｂ側の油路５５ｐと、ロッカシャフト４０側の油路５５ｑと、他方の出力部材２６ｂ側の油路５５ｒとを含み構成されている。そして、他方の出力部材２６ｂ側の油路５５ｒの開口は、該他方の出力部材２６ｂが揺動しても常にロッカシャフト４０側の油路５５ｑの開口と連通するよう、該揺動する範囲に対応して支点穴２７の周方向に長く開口している。   The hydraulic mechanism 52 is interposed between the hydraulic chamber 53 provided inside the other output member 26b that drives the connecting pins 51a and 51b with hydraulic pressure, and the hydraulic chamber 53 and the second connecting pin 51b. An oil for supplying hydraulic pressure to the hydraulic chamber 53 provided through the hydraulic pin 54 for closing the hydraulic chamber 53 and the cylinder head 6, the other lash adjuster 30b, the rocker shaft 40, and the other output member 26b. And a path 55. Therefore, the oil passage 55 includes an oil passage (not shown) on the cylinder head 6 side, an oil passage 55p on the other lash adjuster 30b side, an oil passage 55q on the rocker shaft 40 side, and an oil on the other output member 26b side. And a path 55r. The opening of the oil passage 55r on the other output member 26b side is within the swinging range so as to always communicate with the opening of the oil passage 55q on the rocker shaft 40 side even if the other output member 26b swings. Correspondingly, it opens long in the circumferential direction of the fulcrum hole 27.

本実施例では、ロッカアーム２０が一本のロッカシャフト４０を介して一対のラッシュアジャスタ３０ａ，３０ｂに支持されているため、一本のラッシュアジャスタに支持されている場合に比べて、該ロッカアーム２０が幅方向へ傾き難い。また、それとともに、一対のラッシュアジャスタ３０ａ，３０ｂはロッカシャフト４０によって橋渡しされるているため、該一対のラッシュアジャスタ３０ａ，３０ｂのリークダウン量の差が小さい。そのため、ロッカアーム２０による一対のバルブ８，８のリフト量がバルブ間でずれ難い。   In the present embodiment, since the rocker arm 20 is supported by the pair of lash adjusters 30a and 30b via the single rocker shaft 40, the rocker arm 20 is compared with the case where it is supported by the single lash adjuster. It is difficult to tilt in the width direction. In addition, since the pair of lash adjusters 30a and 30b is bridged by the rocker shaft 40, the difference in the amount of leak-down between the pair of lash adjusters 30a and 30b is small. Therefore, the lift amount of the pair of valves 8 and 8 by the rocker arm 20 is difficult to shift between the valves.

また、本実施例では、ロッカアーム２０がロッカシャフト４０を介して上部リング型のラッシュアジャスタ３０ａ，３０ｂに支持されているため、上部半球型のラッシュアジャスタの上に直接載置されて支持されている場合に比べて、ロッカアーム２０が、ばらけ難い。   In the present embodiment, the rocker arm 20 is supported by the upper ring type lash adjusters 30a and 30b via the rocker shaft 40, so that the rocker arm 20 is directly placed and supported on the upper hemispherical type lash adjuster. Compared to the case, the rocker arm 20 is not easily separated.

また、本実施例では、シャフト固定部４１があるため、ラッシュアジャスタ３０ａ，３０ｂに対するロッカシャフト４０の回動及び該シャフトの長さ方向への変位が規制され、摩耗の増加及び運動性の悪化が軽減される。また、それに加え、該回動及び変位が規制されることによって、他方のラッシュアジャスタ３０ｂ側の油路５５ｐとロッカシャフト４０側の油路５５ｑとの油路どうしのラップ量が、安定して確保される。   Further, in this embodiment, since the shaft fixing portion 41 is provided, the rotation of the rocker shaft 40 relative to the lash adjusters 30a and 30b and the displacement in the length direction of the shaft are restricted, and the increase in wear and the deterioration of the mobility are caused. It is reduced. In addition, by restricting the rotation and displacement, the amount of lap between the oil passages 55p on the other lash adjuster 30b side and the oil passage 55q on the rocker shaft 40 side can be stably secured. Is done.

また、本実施例では、アーム係止部４６があるため、ロッカアーム２０のロッカシャフト４０に対する該シャフトの長さ方向への変位が規制され、該ロッカシャフト４０によるロッカアーム２０の支持が安定化される。また、それに加え、該変位が規制されることによって、ロッカシャフト４０側の油路５５ｑと他方の出力部材２６ｂ側の油路５５ｒとの油路どうしのラップ量が、安定して確保される。   Further, in this embodiment, since the arm locking portion 46 is provided, the displacement of the rocker arm 20 in the length direction of the rocker shaft 40 is restricted, and the support of the rocker arm 20 by the rocker shaft 40 is stabilized. . In addition, by restricting the displacement, the amount of wrap between the oil passages 55q on the rocker shaft 40 side and the oil passage 55r on the other output member 26b side is stably secured.

また、本実施例では、切換機構５０は、ロッカアーム２０の内部に油圧室５３を備えているため、ロッカアーム２０の外部に、連結ピン５１ａ，５１ｂを駆動するピン駆動機構を別途設ける必要性がなく、よって、該切換機構５０の構造が簡単になっている。また、該切換機構５０の油路５５は、油圧式のラッシュアジャスタ３０ｂを経由しているため、該切換機構５０のための油路５５とラッシュアジャスタ３０ｂのための油路との間での油路の共有化が可能な範囲内で極力図られ、このことからも、動弁機構９の構造が簡単になっている。   In the present embodiment, since the switching mechanism 50 includes the hydraulic chamber 53 inside the rocker arm 20, there is no need to separately provide a pin driving mechanism for driving the connecting pins 51 a and 51 b outside the rocker arm 20. Therefore, the structure of the switching mechanism 50 is simplified. Further, since the oil passage 55 of the switching mechanism 50 passes through the hydraulic lash adjuster 30b, the oil between the oil passage 55 for the switching mechanism 50 and the oil passage for the lash adjuster 30b. As much as possible within the range in which the road can be shared, the structure of the valve mechanism 9 is also simplified.

なお、本発明は前記実施例の構成に限定されるものではなく、発明の趣旨から逸脱しない範囲で変更して具体化することもでき、例えば、ロッカシャフト４０に２弁一体型の可変式のロッカアーム２０を支持する代わりに、図５（ａ）に示すように、２弁一体型の非可変式のロッカアーム７０を支持したり、図５（ｂ）に示すように、一対のバルブ８，８をそれぞれ駆動する一対の１弁型の非可変式のロッカアーム８０，８０を支持し、カムシャフト１０ｘに、一の回転カム１０の代わりに、一対のロッカアーム８０，８０をそれぞれ駆動する一対の回転カムを設けてもよい。   It should be noted that the present invention is not limited to the configuration of the above-described embodiment, and can be modified and embodied without departing from the spirit of the invention. For example, the rocker shaft 40 is a two-valve integrated variable type. Instead of supporting the rocker arm 20, as shown in FIG. 5 (a), a two-valve integrated non-variable rocker arm 70 is supported, or as shown in FIG. 5 (b), a pair of valves 8, 8 is supported. A pair of one-valve type non-variable rocker arms 80 and 80 are respectively supported, and a pair of rotating cams that respectively drive the pair of rocker arms 80 and 80 instead of the one rotating cam 10 on the camshaft 10x. May be provided.

本発明の実施例の可変動弁機構を示す斜視図である。It is a perspective view which shows the variable valve mechanism of the Example of this invention. 同実施例の可変動弁機構を示す分解斜視図である。It is a disassembled perspective view which shows the variable valve mechanism of the Example. 同実施例の可変動弁機構を示す背面断面図である。It is a back sectional view showing the variable valve mechanism of the example. 同実施例において、（ａ）は入力アームと出力アームとが非連結状態の時の様子を示す平面断面図、（ｂ）は連結状態の時の様子を示す平面断面図である。In the same Example, (a) is a plane sectional view showing a state when the input arm and the output arm are in a non-connected state, and (b) is a plan sectional view showing a state in a connected state. 同実施例の変更例を示す平面断面図である。It is a plane sectional view showing the example of a change of the example. 従来例の可変動弁機構を示す斜視図である。It is a perspective view which shows the variable valve mechanism of a prior art example.

符号の説明Explanation of symbols

５ シリンダ（気筒）
８ バルブ
９ 動弁機構
１０ 回転カム
２０ ロッカアーム
３０ａ 一方のラッシュアジャスタ
３０ｂ 他方のラッシュアジャスタ
４０ ロッカシャフト
７０ ロッカアーム
８０ ロッカアーム 5 cylinders
8 Valve 9 Valve mechanism 10 Rotating cam 20 Rocker arm 30a One lash adjuster 30b The other lash adjuster 40 Rocker shaft 70 Rocker arm 80 Rocker arm

Claims (1)

一対のラッシュアジャスタが間隔をおいて設置され、該一対のラッシュアジャスタに一本のロッカシャフトが支持され、該一本のロッカシャフトに、同一気筒に対する複数のバルブを駆動する一又は複数のロッカアームが揺動可能に軸支されてなる動弁機構。   A pair of lash adjusters are installed at intervals, and one rocker shaft is supported by the pair of lash adjusters, and one or more rocker arms that drive a plurality of valves for the same cylinder are mounted on the one rocker shaft. A valve operating mechanism that is pivotally supported.
JP2008041986A 2008-02-22 2008-02-22 Valve mechanism Expired - Fee Related JP5252946B2 (en)

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JP2018105174A (en) * 2016-12-26 2018-07-05 トヨタ自動車株式会社 Variable valve mechanism for engine
CN111164279A (en) * 2017-08-25 2020-05-15 伊顿智能动力有限公司 Low stroke deactivation lash adjuster in combination with two-step variable valve lift rocker arm

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Publication number Priority date Publication date Assignee Title
JP2018105174A (en) * 2016-12-26 2018-07-05 トヨタ自動車株式会社 Variable valve mechanism for engine
CN111164279A (en) * 2017-08-25 2020-05-15 伊顿智能动力有限公司 Low stroke deactivation lash adjuster in combination with two-step variable valve lift rocker arm

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