JPH0335484B2 - - Google Patents
Info
- Publication number
- JPH0335484B2 JPH0335484B2 JP57133377A JP13337782A JPH0335484B2 JP H0335484 B2 JPH0335484 B2 JP H0335484B2 JP 57133377 A JP57133377 A JP 57133377A JP 13337782 A JP13337782 A JP 13337782A JP H0335484 B2 JPH0335484 B2 JP H0335484B2
- Authority
- JP
- Japan
- Prior art keywords
- valve
- oil passage
- plunger
- passage slit
- cage
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Lifetime
Links
- 238000005498 polishing Methods 0.000 description 4
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000007423 decrease Effects 0.000 description 3
- 230000008030 elimination Effects 0.000 description 3
- 238000003379 elimination reaction Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 102100025490 Slit homolog 1 protein Human genes 0.000 description 1
- 101710123186 Slit homolog 1 protein Proteins 0.000 description 1
- 230000015572 biosynthetic process Effects 0.000 description 1
- 238000006243 chemical reaction Methods 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 230000005489 elastic deformation Effects 0.000 description 1
- 230000001771 impaired effect Effects 0.000 description 1
- 238000000034 method Methods 0.000 description 1
- 238000007517 polishing process Methods 0.000 description 1
Classifications
-
- 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
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Description
【発明の詳細な説明】
本発明は、内燃機関の動弁機構中の弁頭間隙を
弾発部材の弾発力と油圧とを自動的に排除し、動
弁機構を常に静粛に作動するようにした動弁機構
における油圧式弁頭間隙排除装置に関するもので
ある。DETAILED DESCRIPTION OF THE INVENTION The present invention automatically eliminates the elastic force of an elastic member and hydraulic pressure from the valve head gap in a valve mechanism of an internal combustion engine, so that the valve mechanism always operates quietly. The present invention relates to a hydraulic valve head clearance eliminating device in a valve train.
かかる装置として第１〜３図に示すようなもの
が従来より知られている。 Such devices as shown in FIGS. 1 to 3 are conventionally known.
先ず本発明の理解を容易にするためにこの従来
装置の構造について第１〜３図を参照して説明す
ると、弁頭間隙排除装置のハウジングとなるシリ
ンダ１は、上部に開口端１ａを、下部に閉塞端壁
１ｂをもつ有底中空円筒状に形成され、このシリ
ンダ１は機関本体Ｅの支持孔Eaに嵌装される。
前記シリンダ１内にはその開口端１ａより球状端
部２ａをもつプランジヤ２が上下に摺動自在に嵌
合され、このプランジヤ２の内端と、シリンダ１
の閉塞端壁１ｂ間には油圧室３が画成され、また
前記プランジヤ２内には油溜４と、この油溜４を
前記油圧室３に連通する弁孔５とが形成されてい
る。油溜４は、プランジヤ２の側壁に形成した透
孔６、シリンダ１とプランジヤ２との摺動面間に
設けた環状油路７、シリンダ１の側壁に形成した
透孔８およびシリンダ１の外周面に形成した環状
油路９を介して給油路１０に連通していてこの給
油路１０から送られる油で常に満されている。 First, in order to facilitate understanding of the present invention, the structure of this conventional device will be explained with reference to FIGS. The cylinder 1 is formed in the shape of a hollow cylinder with a bottom and a closed end wall 1b, and is fitted into a support hole Ea of the engine body E.
A plunger 2 having a spherical end 2a is fitted into the cylinder 1 so as to be slidable up and down from its open end 1a, and the inner end of the plunger 2 and the cylinder 1
A hydraulic chamber 3 is defined between the closed end walls 1b, and an oil reservoir 4 and a valve hole 5 communicating the oil reservoir 4 with the hydraulic chamber 3 are formed in the plunger 2. The oil reservoir 4 includes a through hole 6 formed in the side wall of the plunger 2, an annular oil passage 7 provided between the sliding surfaces of the cylinder 1 and the plunger 2, a through hole 8 formed in the side wall of the cylinder 1, and the outer periphery of the cylinder 1. It communicates with an oil supply passage 10 via an annular oil passage 9 formed on the surface, and is always filled with oil sent from this oil supply passage 10.
プランジヤ２の内端には、シリンダ１の内端部
の内周壁に形成した段部１ｃと衝合してプランジ
ヤ２の後退限を規制する筒状ストツパ１１が一体
に形成されている。 A cylindrical stopper 11 is integrally formed at the inner end of the plunger 2 and abuts against a step 1c formed on the inner peripheral wall of the inner end of the cylinder 1 to restrict the backward limit of the plunger 2.
前記油圧室３内には、バルブケージ１２が収容
される。このバルブケージ１２は、第２，３図に
示すように帽状をなす主体部１２ａと、この主体
部１２ａの端部より外側方に一体に延設されるフ
ランジ部１２ｂとよりなつている。主体部１２ａ
の側壁の途中から前記フランジ部１２ｂの端縁ま
で複数の通油スリツト１３が縦方向に穿設されて
いる。そして前記フランジ部１２ｂは、前記スト
ツパ１１の内周面に形成したケージ取付部として
の環状係止溝１４に嵌着保持される。 A valve cage 12 is accommodated within the hydraulic chamber 3. As shown in FIGS. 2 and 3, the valve cage 12 is made up of a cap-shaped main body 12a and a flange 12b integrally extending outward from the end of the main body 12a. Main body part 12a
A plurality of oil passage slits 13 are vertically bored from the middle of the side wall to the edge of the flange portion 12b. The flange portion 12b is fitted and held in an annular locking groove 14, which serves as a cage attachment portion, formed on the inner peripheral surface of the stopper 11.
前記バルブケージ１２内には、前記弁孔１５を
開閉するチエツクバルブ１５が浮動状に収容され
ている。このチエツクバルブ１５は油圧室３が減
圧したとき開弁し、また該室３が昇圧したとき閉
弁するもので、その開弁ストロークを規制するた
めのストツパ１６がバルブケージ１２の底部に設
けられている。また前記油圧室３内にはプランジ
ヤ２をシリンダ１の上方に突出させるように付勢
する弾発ばね１７が収納される。この弾発ばね１
７とプランジヤ２の内端面間には、前記バルブケ
ージ１２のフランジ部１２ｂが挟持される。 A check valve 15 for opening and closing the valve hole 15 is housed in the valve cage 12 in a floating manner. This check valve 15 opens when the pressure in the hydraulic chamber 3 decreases, and closes when the pressure in the chamber 3 increases.A stopper 16 is provided at the bottom of the valve cage 12 to restrict the opening stroke. ing. Further, a resilient spring 17 is housed in the hydraulic chamber 3 and urges the plunger 2 to protrude above the cylinder 1. This spring 1
The flange portion 12b of the valve cage 12 is held between the inner end surface of the plunger 7 and the plunger 2.
プランジヤ２は、その球状端部２ａでロツカア
ームＲの基端を支承しており、このロツカアーム
Ｒの揺動先端は内燃機関の吸気または排気ポート
１８を開閉するポペツト弁Ｖの弁頭に当接され、
その中間部にロツカアームＲを揺動させてポペツ
ト弁Ｖを開弁する動弁カムＣが配置される。ポペ
ツト弁Ｖには、通常のようにこれを閉弁方向に付
勢する弁ばねＳが設けられ、この弁ばねＳの弾発
力は前記弾発ばね１７のそれよりもはるかに強力
である。 The plunger 2 supports the base end of a rocker arm R with its spherical end 2a, and the swinging tip of the rocker arm R is brought into contact with the valve head of a poppet valve V that opens and closes the intake or exhaust port 18 of the internal combustion engine. ,
A valve operating cam C that swings the rocker arm R to open the poppet valve V is disposed in the middle thereof. The poppet valve V is provided with a valve spring S which urges it in the valve closing direction as usual, and the elastic force of this valve spring S is much stronger than that of the elastic spring 17.
次にこの従来装置の作用を説明すると、ポペツ
ト弁Ｖが閉じているとき、プランジヤ２は弾発ば
ね１７の弾発力をもつて上昇し、ロツカアームＲ
の基端を押上げ、ロツカアームＲの揺動先端とポ
ペツト弁Ｖの弁頭間の間隙を排除する。このとき
プランジヤ２の上昇に伴い油圧室３内が減圧すれ
ば、チエツクバルブ１５が開弁するので、油溜４
からの油が弁孔５を通して油圧室３内に補給さ
れ、油圧室３内は油によつて満される。 Next, the operation of this conventional device will be explained. When the poppet valve V is closed, the plunger 2 rises with the elastic force of the elastic spring 17, and the rocker arm R
Push up the base end of the rocker arm R to eliminate the gap between the swinging tip of the rocker arm R and the valve head of the poppet valve V. At this time, if the pressure inside the hydraulic chamber 3 decreases as the plunger 2 rises, the check valve 15 opens, so the oil sump 4
Oil is supplied into the hydraulic chamber 3 through the valve hole 5, and the hydraulic chamber 3 is filled with oil.
次に動弁カムＣの回転によりそのカム面がロツ
カアームＲに接触するに至れば、該ロツカアーム
Ｒの中間部が下方に押されてそこに開弁力が働く
と、その反作用としてチエツクバルブ１５により
閉鎖状態とされた油圧室３内に油圧が発生し、こ
の油圧力でプランジヤ２が支持されるので、ロツ
カアームＲはプランジヤ２の球状端部２ａを支点
としてポペツト弁Ｖ側に揺動し、弁ばねＳの弾発
力に抗してポペツト弁Ｖを開く。この間油圧室３
の油はシリンダ１とプランジヤ２との摺動面間よ
り僅かに漏洩するが、その漏洩分は次回のポペツ
ト弁Ｖの閉鎖時に油溜４より補給される。 Next, when the cam surface of the valve drive cam C comes into contact with the rocker arm R due to the rotation of the valve drive cam C, the middle part of the rocker arm R is pushed downward and a valve opening force is applied thereto, and as a reaction, the check valve 15 is activated. Hydraulic pressure is generated in the closed hydraulic chamber 3, and the plunger 2 is supported by this hydraulic pressure, so the rocker arm R swings toward the poppet valve V using the spherical end 2a of the plunger 2 as a fulcrum, and the valve is closed. The poppet valve V is opened against the elastic force of the spring S. During this time, hydraulic chamber 3
A small amount of oil leaks from between the sliding surfaces of the cylinder 1 and the plunger 2, but the leaked amount is replenished from the oil reservoir 4 the next time the poppet valve V is closed.
ところでかかる弁頭間〓排除装置では、油圧室
３が減圧されてチエツクバルブ１５が開いたと
き、油溜４内の油が前記バルブケージ１２の通油
スリツト１３を通つて油圧室３内に補給される
が、その補給時間は短く、特に内燃機関が高速回
転されるときは、極端に短くなるので、前記バル
ブケージ１２の通油スリツト１３の開口面積をで
きるだけ大きく設定することが望ましい。そのた
め前記通油スリツト１３はその幅Ｗを広く、かつ
その長さＬを長く、すなわちバルブケージ１２の
主体部１２ａからフランジ部１２ｂにかけて穿設
する必要がある。しかしながら前記通油スリツト
１３を大きくしすぎると、バルブケージ１２自体
の強度が損われる不都合が生じる。 By the way, in such a valve head elimination device, when the pressure in the hydraulic chamber 3 is reduced and the check valve 15 is opened, the oil in the oil reservoir 4 is replenished into the hydraulic chamber 3 through the oil passage slit 13 of the valve cage 12. However, the replenishment time is short, and becomes extremely short especially when the internal combustion engine is rotated at high speed. Therefore, it is desirable to set the opening area of the oil passage slit 13 of the valve cage 12 as large as possible. Therefore, it is necessary for the oil passage slit 13 to have a wide width W and a long length L, that is, to extend from the main body portion 12a of the valve cage 12 to the flange portion 12b. However, if the oil passage slit 13 is made too large, the strength of the valve cage 12 itself is impaired.
また前記バルブケージ１２は、生産性およびコ
ストの面からプレス加工により生産されるが、そ
の際そのプレス加工を容易にするには前記通油ス
リツト１３はフランジ部１２ｂの端縁に開口する
位置まで形成する必要があるが、そのプレス加工
後のバルブケージ１２のバリ等を最も能率よく除
去するためにはバレル研摩方法（多くの砥石状細
片と多くのバルブケージ１２とを容器に入れて該
容器を回転することにより研摩する方法）が採用
される。この場合通油スリツト１３の、フランジ
部１２ｂの幅Ｗがその厚さＴよりも大きいと、前
述のバレル研摩中、一方のバルブケージ１２の通
油スリツト１３に、他方のバルブケージ１２のフ
ランジ部１２ｂの端縁が噛み込んで、前記研摩後
にそれらを分離する作業が面倒になるばかりでな
くバルブケージ１２の変形を惹起する懸念があ
る。 Further, the valve cage 12 is produced by press working from the viewpoint of productivity and cost, but in order to facilitate the press working, the oil passage slit 13 should be extended to a position where it opens at the edge of the flange portion 12b. However, in order to most efficiently remove burrs etc. from the valve cage 12 after the press processing, the barrel polishing method (many grindstone-like pieces and many valve cages 12 are placed in a container and then removed) is used. A method of polishing by rotating the container) is adopted. In this case, if the width W of the flange portion 12b of the oil passage slit 13 is larger than its thickness T, during the above-mentioned barrel polishing, the oil passage slit 13 of one valve cage 12 is attached to the flange portion of the other valve cage 12. There is a concern that the edges of the valve cage 12 may get caught, which not only makes it troublesome to separate them after the polishing, but also causes deformation of the valve cage 12.
本発明は上記に鑑み提案されたもので、従来装
置の上記問題を解決し得る、動弁機構における油
圧式弁頭間隙排除装置を提供することを目的とす
る。 The present invention has been proposed in view of the above, and an object of the present invention is to provide a hydraulic valve head gap eliminating device for a valve train, which can solve the above-mentioned problems of conventional devices.
そしてこの目的を達成するために本発明によれ
ば、シリンダ内にプランジヤを摺動自在に嵌合
し、シリンダとプランジヤ間に油圧室を画成し、
この油圧室をプランジヤに形成した弁孔を介して
油溜に連通し、前記弁孔には油圧室の減圧時に開
弁され、またその昇圧時に閉弁されるチエツクバ
ルブを設け、前記油圧室内において前記チエエツ
クバルブを収容保持するバルブケージを、帽状の
主体部と、この主体部の端部より外側方に一体に
延設されて前記プランジヤのケージ取付部に嵌着
されたフランジ部とより構成し、前記プランジヤ
は、弾発部材によりシリンダより外方に突出する
ように付勢されてその外端に動弁機構のロツカア
ームを支承し、該機構の動弁カムの開弁力が前記
プランジヤに軸方向の押圧力として作用するよう
にした、動弁機構における油圧式弁頭間〓排除装
置において、バルブケージの前記主体部には、主
通油スリツトを、また前記フランジ部には、前記
主通油スリツトに連なり且つ該フランジ部の端縁
に開口する端部通油スリツトをそれぞれ形成し、
該端部通油スリツトは前記主通油スリツトよりも
幅狭で、且つ前記フランジ部の厚さよりも細く形
成される。 In order to achieve this object, according to the present invention, a plunger is slidably fitted into a cylinder, and a hydraulic chamber is defined between the cylinder and the plunger,
This hydraulic chamber is communicated with an oil reservoir through a valve hole formed in the plunger, and the valve hole is provided with a check valve that is opened when the pressure in the hydraulic chamber is reduced and closed when the pressure is increased. A valve cage that accommodates and holds the check valve is composed of a cap-shaped main body and a flange that integrally extends outward from an end of the main body and is fitted into a cage mounting portion of the plunger. , the plunger is urged to protrude outward from the cylinder by a resilient member, and supports a rocker arm of the valve mechanism at its outer end, and the valve opening force of the valve drive cam of the mechanism is applied to the plunger. In a hydraulic valve head clearance device in a valve train which acts as a pressing force in a direction, the main body portion of the valve cage is provided with a main oil passage slit, and the flange portion is provided with a main oil passage slit. forming end oil passage slits that are continuous with the oil slits and open at the edge of the flange portion;
The end oil passage slit is narrower than the main oil passage slit and thinner than the thickness of the flange portion.
以下、第４，５図を参照して本発明の一実施例
について説明すると、動弁機構の弁頭間隙排除装
置は、バルブケージの構成を除いて前記従来装置
と全く同じものであり、そのバルブケージ１２′
は、前記従来装置のそれと同じく帽状の主体部１
２′ａの端縁に外側方にのびる環状のフランジ部
１２′ｂを一体に延設して構成され、これらに亘
つて通油スリツト１３′が穿設される。即ち前記
主体部１２′ａの側壁には周方向に間隔を存して
縦方向に複数の主通油スリツト１３′ａが穿設さ
れ、また前記フランジ部１２′ｂには、前記主通
油スリツト１３′ａに連なり、該フランジ部１
２′ｂの端縁に開口する端部通油スリツト１３′ｂ
が穿設されている。端部通油スリツト１３′ｂの
幅W′は、主通油スリツト１３′ａよりも幅狭で、
且つフランジ部１２′ｂの厚さT′よりも細く形成
される。そして通油スリツト１３′の全体の通路
面積を大きくすることと、バルブケージ１２′の
絞り加工時および使用時に応力集中が発生するこ
とがないようにするために、主通油スリツト１
３′ａと端部通油スリツト１３′ｂとの面積変化の
境界点Ｐをフランジ部１２′ｂに位置させる。す
なわち主体部１２′ａの最大半径R2と前記面積変
化の境界点Ｐまでの距離Ａを、フランジ部１２′
ｂの半径R1と前記主体部１２′ａの最大半径R2と
の差R1−R2よりも小さくし、かつ主体部１２′ａ
とフランジ部１２′ｂとの外周側接続部のアール
ｒの半径よりも大きくなるように設定する。以上
により面積変化の境界点Ｐは、主体部１２′ａと
フランジ部１２′ｂとの接続湾曲部には位置しな
くなり、バルブケージ１２′の絞りプレス加工お
よび使用時の応力集中が避けられる。 Hereinafter, one embodiment of the present invention will be described with reference to FIGS. 4 and 5. The valve head clearance elimination device of the valve train is completely the same as the conventional device except for the structure of the valve cage. Valve cage 12'
The main body part 1 has a cap-like shape similar to that of the conventional device.
An annular flange portion 12'b extending outwardly extends integrally with the end edge of 2'a, and an oil passage slit 13' is bored across the flange portion 12'b. That is, a plurality of main oil passage slits 13'a are vertically bored at intervals in the circumferential direction in the side wall of the main body part 12'a, and the main oil passage slits 13'a are formed in the flange part 12'b. Continuing with the slit 13'a, the flange portion 1
End oil passage slit 13'b opened at the edge of 2'b
is drilled. The width W' of the end oil passage slit 13'b is narrower than the main oil passage slit 13'a,
Moreover, it is formed to be thinner than the thickness T' of the flange portion 12'b. In order to increase the overall passage area of the oil passage slit 13' and to prevent stress concentration from occurring during drawing and use of the valve cage 12', the main oil passage slit 1
The boundary point P of the area change between 3'a and the end oil passage slit 13'b is located at the flange portion 12'b. In other words, the distance A between the maximum radius R 2 of the main body part 12'a and the boundary point P of the area change is determined by the flange part 12'
b is smaller than the difference R 1 −R 2 between the radius R 1 of the main body portion 12′a and the maximum radius R 2 of the main body portion 12′a, and
and the flange portion 12'b are set to be larger than the radius r of the outer peripheral side connecting portion. As a result of the above, the boundary point P of area change is no longer located at the connecting curved portion between the main body portion 12'a and the flange portion 12'b, and stress concentration during drawing press processing and use of the valve cage 12' can be avoided.
以上のように本発明によれば、バルブケージ
の、帽状をなす主体部には主通油スリツトを、ま
たプランジヤのケージ取付部に嵌着されるフラン
ジ部には、前記主通油スリツトに連なり、該フラ
ンジ部の端縁に開口する端部通油スリツトをそれ
ぞれ形成し、該端部通油スリツトは前記主通油ス
リツトよりも幅狭で、かつ前記フランジ部の厚さ
よりも細く形成されるので、
上記主通油スリツト及び端部通油スリツトよ
りなる通油スリツトは、全体として所要量の油
が通過するのに必要十分な通路面積を確保して
油圧式弁頭間隙排除装置の所期の高性能を確保
しつつ、該スリツトの形成に伴うバルブケージ
の強度低下を最小限に留めてバルブケージの強
度アツプに寄与することができる。 As described above, according to the present invention, the main oil passage slit is provided in the cap-shaped main body portion of the valve cage, and the main oil passage slit is provided in the flange portion fitted to the cage mounting portion of the plunger. The end oil passing slits are connected to each other to form end oil passing slits that open at the edges of the flange portion, and the end oil passing slits are narrower than the main oil passing slits and thinner than the thickness of the flange portion. Therefore, the oil passage slit, which consists of the main oil passage slit and the end oil passage slit, secures a sufficient passage area for the required amount of oil to pass through, and is suitable for the hydraulic valve head clearance removal device. This contributes to increasing the strength of the valve cage by minimizing the decrease in strength of the valve cage due to the formation of the slits while ensuring high performance during the period.
上記通油スリツトをフランジ部端縁に開口さ
せたことにより、そのフランジ部の径方向弾性
変形が無理なく許容されて、プランジヤのケー
ジ取付部に対する該フランジ部の取付性を向上
させることができ、その上、該フランジ部端縁
にスリツトを開口させない構造のものに比べて
バルブケージの成型性が良好であるから、各部
の寸法精度が高いバルブケージを得ることがで
きる。 By opening the oil passage slit at the edge of the flange portion, elastic deformation in the radial direction of the flange portion is easily allowed, and the mountability of the flange portion to the cage attachment portion of the plunger can be improved; Furthermore, since the moldability of the valve cage is better than that of a structure in which slits are not opened at the edge of the flange portion, it is possible to obtain a valve cage with high dimensional accuracy in each part.
上記通油スリツトをフランジ部端縁に開口さ
せたにも拘わらず、端部通油スリツトの上記寸
法限定によつて、前述のバレル研摩時における
バルブケージ同志の噛み込みをなくすることが
できるから、該バルブケージの生産性を高めて
そのコストダウンを図ることができ、しかもそ
の噛み込みに起因したバルブケージの変形を未
然に防止することができる。 Even though the oil passage slit is opened at the end edge of the flange part, by limiting the dimensions of the end oil passage slit, it is possible to prevent the valve cages from getting caught together during barrel polishing as described above. , it is possible to increase the productivity of the valve cage and reduce its cost, and furthermore, it is possible to prevent the valve cage from being deformed due to the jamming.
等の諸効果を達成し得る。The following effects can be achieved.
第１図は従来の弁頭間隙排除装置の縦断面図、
第２図は従来のバルブケージの平面図、第３図は
その縦断面図、第４，５図は本発明の実施例を示
すもので、第４図はバルブケージの平面図、第５
図はその縦断側面図である。
Ｃ…動弁カム、Ｒ…ロツカアーム、１…シリン
ダ、２…プランジヤ、３…油圧室、４…油溜、５
…弁孔、１２′…バルブケージ、１２′ａ…主体
部、１２′ｂ…フランジ部、１３′…通油スリツ
ト、１３′ａ…主通油スリツト、１３′ｂ…端部通
油スリツト、１４…ケージ取付部としての環状係
止溝、１５…チエツクバルブ、１７…弾発ばね
（弾発部材）。
Figure 1 is a longitudinal cross-sectional view of a conventional valve head gap elimination device.
FIG. 2 is a plan view of a conventional valve cage, FIG. 3 is a vertical sectional view thereof, and FIGS. 4 and 5 show an embodiment of the present invention. FIG.
The figure is a longitudinal side view. C...Valve train cam, R...Rocker arm, 1...Cylinder, 2...Plunger, 3...Hydraulic chamber, 4...Oil sump, 5
... Valve hole, 12'... Valve cage, 12'a... Main body part, 12'b... Flange part, 13'... Oil passage slit, 13'a... Main oil passage slit, 13'b... End oil passage slit, 14... Annular locking groove as a cage attachment part, 15... Check valve, 17... Resilient spring (resilient member).
Claims (1)
合し、シリンダ１とプランジヤ２間に油圧室３を
画成し、この油圧室３をプランジヤ２に形成した
弁孔５を介して油溜４に連通し、前記弁孔５には
前記油圧室３の減圧時に開弁され、またその昇圧
時に閉弁されるチエツクバルブ１５を設け、前記
油圧室３内において前記チエツクバルブ１５を収
容保持するバルブケージ１２′を、帽状の主体部
１２′ａと、この主体部１２′ａの端部より外側方
に一体に延設されて前記プランジヤ２のケージ取
付部１４に嵌着されたフランジ部１２′ｂとより
構成し、前記プランジヤ２は、弾発部材１７によ
りシリンダ１より外方に突出するように付勢され
てその外端に動弁機構のロツカアームＲを支承
し、該機構の動弁カムＣの開弁力が前記プランジ
ヤ２に軸方向の押圧力として作用するようにし
た、動弁機構における油圧式弁頭間隙排除装置に
おいて、バルブケージ１２′の前記主体部１２′ａ
には、主通油スリツト１３′ａを、また前記フラ
ンジ部１２′ｂには、前記主通油スリツト１３′ａ
に連なり且つ該フランジ部１２′ｂの端縁に開口
する端部通油スリツト１３′ｂをそれぞれ形成し、
該端部通油スリツト１３′ｂは前記主通油スリツ
ト１３′ａよりも幅狭で、且つ前記フランジ部１
２′ｂの厚さT′よりも細く形成してなる、動弁機
構における油圧式弁頭間隙排除装置。1 A plunger 2 is slidably fitted into a cylinder 1, a hydraulic chamber 3 is defined between the cylinder 1 and the plunger 2, and an oil reservoir 4 is formed in this hydraulic chamber 3 via a valve hole 5 formed in the plunger 2. The valve hole 5 is provided with a check valve 15 which is opened when the pressure in the hydraulic chamber 3 is reduced and closed when the pressure is increased. The cage 12' includes a cap-shaped main body part 12'a, and a flange part 12 that integrally extends outward from the end of the main body part 12'a and is fitted into the cage attachment part 14 of the plunger 2. 'b, the plunger 2 is urged by a resilient member 17 to protrude outward from the cylinder 1, supports the rocker arm R of the valve mechanism at its outer end, and supports the rocker arm R of the valve mechanism. In a hydraulic valve head gap eliminating device in a valve operating mechanism in which the valve opening force of a cam C acts on the plunger 2 as an axial pressing force, the main body portion 12'a of the valve cage 12'
The main oil passage slit 13'a is provided in the flange portion 12'b, and the main oil passage slit 13'a is provided in the flange portion 12'b.
forming end oil passage slits 13'b that are continuous with and open at the edge of the flange portion 12'b,
The end oil passage slit 13'b is narrower than the main oil passage slit 13'a, and is narrower than the main oil passage slit 13'a.
A hydraulic valve head gap eliminating device in a valve train, which is formed to be thinner than the thickness T' of 2'b.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13337782A JPS5923013A (en) | 1982-07-30 | 1982-07-30 | Valve cage of oil pressure type valve head gap removing device in valve moving mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP13337782A JPS5923013A (en) | 1982-07-30 | 1982-07-30 | Valve cage of oil pressure type valve head gap removing device in valve moving mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5923013A JPS5923013A (en) | 1984-02-06 |
| JPH0335484B2 true JPH0335484B2 (en) | 1991-05-28 |
Family
ID=15103309
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP13337782A Granted JPS5923013A (en) | 1982-07-30 | 1982-07-30 | Valve cage of oil pressure type valve head gap removing device in valve moving mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5923013A (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP5358265B2 (en) * | 2009-04-24 | 2013-12-04 | トヨタ自動車株式会社 | Rush adjuster and its assembly method |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5611301B2 (en) * | 1975-12-11 | 1981-03-13 |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5910327Y2 (en) * | 1979-07-04 | 1984-04-02 | エヌ・テ−・エヌ東洋ベアリング株式会社 | Valve gap automatic adjustment device |
| JPS572203U (en) * | 1980-06-03 | 1982-01-07 |
-
1982
- 1982-07-30 JP JP13337782A patent/JPS5923013A/en active Granted
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5611301B2 (en) * | 1975-12-11 | 1981-03-13 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5923013A (en) | 1984-02-06 |
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