JPH0222205B2 - - Google Patents
Info
- Publication number
- JPH0222205B2 JPH0222205B2 JP23133785A JP23133785A JPH0222205B2 JP H0222205 B2 JPH0222205 B2 JP H0222205B2 JP 23133785 A JP23133785 A JP 23133785A JP 23133785 A JP23133785 A JP 23133785A JP H0222205 B2 JPH0222205 B2 JP H0222205B2
- Authority
- JP
- Japan
- Prior art keywords
- spherical
- concave
- convex portion
- rocker arm
- contact
- 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
Links
- 239000003921 oil Substances 0.000 description 8
- 238000005498 polishing Methods 0.000 description 6
- 238000003754 machining Methods 0.000 description 5
- 238000004519 manufacturing process Methods 0.000 description 3
- 238000003825 pressing Methods 0.000 description 3
- 238000005255 carburizing Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 238000010438 heat treatment Methods 0.000 description 2
- 238000010791 quenching Methods 0.000 description 2
- 230000000171 quenching effect Effects 0.000 description 2
- NCGICGYLBXGBGN-UHFFFAOYSA-N 3-morpholin-4-yl-1-oxa-3-azonia-2-azanidacyclopent-3-en-5-imine;hydrochloride Chemical compound Cl.[N-]1OC(=N)C=[N+]1N1CCOCC1 NCGICGYLBXGBGN-UHFFFAOYSA-N 0.000 description 1
- 238000013459 approach Methods 0.000 description 1
- 239000010687 lubricating oil Substances 0.000 description 1
- 238000005121 nitriding Methods 0.000 description 1
Landscapes
- Pivots And Pivotal Connections (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
Description
【発明の詳細な説明】
産業上の利用分野
本発明は、球面凸部とこれを受ける凹面受座と
よりなるエンジン動弁装置のタペツト支持部また
は球面接手等の球面対偶に関するものである。DETAILED DESCRIPTION OF THE INVENTION Field of the Invention The present invention relates to a spherical pair such as a tappet support part or a spherical hand for an engine valve operating system, which comprises a spherical convex part and a concave seat for receiving the convex part.
従来技術
球面対偶では、点接触させずに接触部の単位面
積当りの押付け力を小さくし、これに加わる荷重
を無理なく支持する必要があるため、理論的に考
えると、その球面凸部と、この球面凸部を受けて
これを支持する球面受座とは、同一径であること
が好ましい。Prior Art In a spherical pair, it is necessary to reduce the pressing force per unit area of the contact part without making point contact, and to support the load applied to it without difficulty. It is preferable that the spherical seat that receives and supports this spherical convex portion has the same diameter.
しかしながら、球面凸部と球面受座の径を同一
にした場合、機械加工後の熱処理に伴う歪や、加
工公差等の原因により、球面凸部が部分的でも僅
かに大きくなり、この球面凸部が球面受座に嵌合
することが不可能であり、球面対偶の役を果すこ
とができず、従来では、下記に説明するように、
一定の大きさの半径差をもつて球面対偶を構成し
ていた。 However, when the diameters of the spherical convex part and the spherical catch are made the same, the spherical convex part becomes slightly larger even in parts due to distortion caused by heat treatment after machining, processing tolerances, etc. It is impossible to fit into the spherical catch and cannot function as a spherical pair, and conventionally, as explained below,
They formed a spherical pair with a fixed radius difference.
即ち、第１図に誇張して図示するように、球面
凸部０１の半径r1よりも球面受座０２の半径r2を
僅かに大きく設定し、この差をできる限り小さく
し、球面凸部０１と球面受座０２との接触面積を
できる限り広く取るようにしていた。 In other words , as shown in an exaggerated manner in FIG. The contact area between 01 and the spherical seat 02 was made as wide as possible.
ところが、このような球面対偶は、本質的に底
面での点接触に近い接触面積しか確保できず、接
触部での応力集中を招き、接触面を充分に潤滑で
きなくなり、さらに横方向の安定が悪く、しかも
球面凸部０１および球面受座０２の表面の僅かな
凹凸によりその接触位置が一定しない難点があつ
た。 However, such a spherical pair essentially can only secure a contact area close to a point contact on the bottom surface, leading to stress concentration at the contact area, making it impossible to lubricate the contact surface sufficiently, and furthermore, lateral stability is reduced. Moreover, there was a problem that the contact position was not constant due to slight irregularities on the surfaces of the spherical convex portion 01 and the spherical seat 02.
さらにこの接触底面を潤滑油路等で逃がし加工
する場合があるが、球面凸部０１が角部で受ける
ことになり、摩耗が激しく、耐久上問題がある。 Furthermore, this contact bottom surface may be machined to provide relief with a lubricating oil path, but the spherical convex portion 01 is received at the corner, resulting in severe wear and durability problems.
これを改良したものとして、本出願人は第２図
に図示したような球面対偶に関する出願（特願昭
59−203737号（特開昭61−81503号公報参照））を
既に行つた。 As an improvement on this, the present applicant has applied for a spherical pair as shown in FIG.
No. 59-203737 (see Japanese Patent Application Laid-Open No. 61-81503)).
この球面対偶では、球面対偶の中心軸０５に対
しεだけ右方に偏心した点０６を中心とし、球面
凸部０４の半径r3よりも僅かに大きな半径r4の円
で中心軸０５より右方に画いた円弧０７ｌと、中
心軸０５に対しこの円弧０７ｌと対称な円弧０７
ｒとを母線とし中心軸０５を回転中心とした回転
体面をなした工具でもつて球面受座０３を形成し
た。 In this spherical pair, the center is a point 06 which is eccentric to the right by ε with respect to the central axis 05 of the spherical pair, and the circle has a radius r 4 slightly larger than the radius r 3 of the spherical convex portion 04 and is located to the right of the central axis 05. An arc 07l drawn in the direction, and an arc 07 symmetrical to this arc 07l with respect to the central axis 05.
The spherical seat 03 was also formed using a tool having a rotating body surface with the generatrix r and the central axis 05 as the center of rotation.
発明が解決しようとする問題点
このような球面対偶においては、球面受座０３
と球面凸部０４との接触点０８と球面凸部０４の
中心０９とを結ぶ線と球面対偶中心軸０５とのな
す角αは、理論的には、
（r4−r3）sinα＝εより
α＝sin-1ε／r4−r3
として求められるものの、工具の曲率半径r4およ
びその偏心量εを実際に正確に測定できないた
め、接触角αを求めることができず、しかもこの
ような非球面状工具を製作することが困難であつ
て加工精度を厳しく管理できず、さらに工具が摩
耗すると、その曲率半径が小さくなつて加工に適
合しえなくなり、工具の寿命が短かつた。Problems to be solved by the invention In such a spherical pair, the spherical catch 03
Theoretically, the angle α formed by the line connecting the contact point 08 of the spherical convex portion 04 with the center 09 of the spherical convex portion 04 and the spherical pair central axis 05 is (r 4 − r 3 ) sin α = ε Although it can be found as α=sin -1 ε/r 4 −r 3 , since the radius of curvature r 4 of the tool and its eccentricity ε cannot be actually measured accurately, the contact angle α cannot be determined, and furthermore, this It is difficult to manufacture such aspherical tools, and machining accuracy cannot be strictly controlled.Furthermore, when the tool wears, its radius of curvature becomes smaller and becomes unsuitable for machining, resulting in a shortened tool life. .
またこのような加工を施した球面受座０３を熱
処理した後、この熱処理による歪を除去するため
に、これを研磨しにくい。 Furthermore, after the spherical seat 03 that has been processed in this way is heat treated, it is difficult to polish it in order to remove the distortion caused by the heat treatment.
問題点を解決するための手段および作用
本発明はこのような難点を克服した球面対偶の
改良に係り、球体または少なくとも接触部表面が
凸球面の一部である球面凸部と、該球面凸部を受
けてこれを支持する凹面受座とよりなる球面対偶
において、該凹面受座の一部底面側を前記球面凸
部より径の小さな凹球面に形成し、該底面側の凹
球面より凹面受座の開口側を前記球面凸部より径
の大きな凹球面に形成することにより、前記球面
凸部より小さな径の凹球面と該球面凸部より大き
な径の凹球面とが交わる円弧に沿つて該球面凸部
を線接触支持させることができる。Means and Effects for Solving the Problems The present invention relates to an improvement of a spherical pair that overcomes these difficulties, and includes a spherical convex portion whose spherical body or at least a contact surface is a part of the convex spherical surface, and the spherical convex portion. In a spherical pair consisting of a concave seat that receives and supports the concave seat, a part of the bottom side of the concave seat is formed into a concave spherical surface having a diameter smaller than that of the spherical convex portion, and the concave receiver is made smaller than the concave spherical surface on the bottom side. By forming the opening side of the seat to be a concave spherical surface having a larger diameter than the spherical convex portion, the concave spherical surface having a diameter smaller than the spherical convex portion intersects with the concave spherical surface having a larger diameter than the spherical convex portion intersect. The spherical convex portion can be supported in line contact.
また前記２種の凹球面の径の値とその中心位置
関係とを適宜選定すれば、前記球面凸部との接触
角を任意に設定することができる。 Further, by appropriately selecting the values of the diameters of the two types of concave spherical surfaces and their center position relationships, the contact angle with the spherical convex portion can be arbitrarily set.
実施例
以下第３図ないし第５図に図示された本発明の
一実施例について説明する。Embodiment An embodiment of the present invention illustrated in FIGS. 3 to 5 will be described below.
本実施例は、自動車用ガソリンエンジン１の動
弁装置２におけるロツカーアーム３とオイルタペ
ツト４およびプツシユロツド５との接触支持部に
適用されたもので、ロツカーアーム３ａ，３ｂは
カムシヤフト６と一体のカム７に押されて、オイ
ルタペツト４との支持部を中心として揺動され、
ロツカーアーム３ｃはプツシユロツド５に押され
て軸１９を中心として揺動され、吸気弁８はロツ
カーアーム３ａにより直接に開閉駆動されるとと
もに、排気弁９はロツカーアーム３ｂより、プツ
シユロツド５、ロツカーアーム３ｃを介して開閉
駆動されるようになつている。 This embodiment is applied to a contact support portion between a rocker arm 3, an oil tappet 4, and a push rod 5 in a valve train 2 of a gasoline engine 1 for an automobile. and is swung around the support part with the oil tappet 4,
The rocker arm 3c is pushed by the push rod 5 and oscillated about the shaft 19, the intake valve 8 is driven to open and close directly by the rocker arm 3a, and the exhaust valve 9 is opened and closed by the rocker arm 3b via the push rod 5 and the rocker arm 3c. It is becoming driven.
ロツカーアーム３ａ，３ｂとオイルタペツト４
との接触支持部およびロツカーアーム３ｂ，３ｃ
とプツシユロツド５との接触支持部は下記のよう
に球面対偶１０を構成している。 Rocker arms 3a, 3b and oil tappet 4
contact support part and rocker arms 3b, 3c
The contact support portion between the push rod 5 and the push rod 5 constitutes a spherical pair 10 as described below.
オイルタペツト４とプツシユロツド５とに接触
するロツカーアーム３ｂにおいて、オイルタペツ
ト４とに接触支持する球面対偶１０のみについて
説明するが、プツシユロツド５に接触支持する球
面対偶１０および他のロツカーアーム３ａ，３ｃ
における球面対偶１０もロツカーアーム３ｂと球
面対偶１０においてその構成が同様であるので、
省略する。 In the rocker arm 3b that contacts the oil tappet 4 and the push rod 5, only the spherical pair 10 that contacts and supports the oil tappet 4 will be explained, but the spherical pair 10 that contacts and supports the push rod 5 and the other rocker arms 3a, 3c.
Since the configuration of the spherical pair 10 is the same in the Rocker arm 3b and the spherical pair 10,
Omitted.
球面対偶１０は、球面凸部であるボール１１
と、同ボール１１を受けてこれを遊嵌支持する凹
面受座であるロツカーアーム凹部１２とよりな
り、ボール１１の直径Ｄは11.00mmでその公差が
±0.02mmの範囲内に収まるようにボール１１は形
成されている。 The spherical pair 10 has a ball 11 which is a spherical convex portion.
and a rocker arm recess 12 which is a concave seat that receives and supports the ball 11 with a loose fit. is formed.
またロツカーアーム３におけるロツカーアーム
凹部１２の底面側１３の半径ｒは5.40mm、その公
差が±0.02mmの範囲内に収まるように、ロツカー
アーム３のロツカーアーム凹部１２に機械加工が
施され、所要の浸炭焼入処理が施され、次に直径
2Rが11.08mm、その公差が＋0.02mm、−0.04mmの範
囲に収まる図示されない球状工具で球面研磨加工
がロツカーアーム３のロツカーアーム凹部１２に
施され、最後にこのロツカーアーム３のロツカー
アーム凹部１２に軟窒化処理が施される。 In addition, the radius r of the bottom side 13 of the Rocker arm recess 12 in the Rocker arm 3 is 5.40 mm, and the Rocker arm recess 12 of the Rocker arm 3 is machined so that the tolerance is within ±0.02 mm, and the required carburizing and quenching is performed. The treatment is applied and then the diameter
Spherical polishing is performed on the rocker arm recess 12 of the rocker arm 3 using a spherical tool (not shown) with a 2R of 11.08 mm and a tolerance within the range of +0.02 mm and -0.04 mm, and finally the rocker arm recess 12 of the rocker arm 3 is nitrocarburized. Processing is performed.
このような加工が施されたロツカーアーム３の
ロツカーアーム凹部１２においては、その底面側
にボール１１の直径Ｄ＝11.00mmよりも小径の2r
＝10.80mmの第１の凹球面１３が形成され、その
底面側凹球面１３よりロツカーアーム凹部１２の
開口側にボール１１の直径Ｄ＝11.00mmよりも大
径の2R＝11.08mmの第２の凹球面１４が形成され
る。 In the rocker arm recess 12 of the rocker arm 3 processed in this way, there is a 2r diameter smaller than the diameter D of the ball 11, D = 11.00 mm, on the bottom side.
A first concave spherical surface 13 with a diameter of =10.80 mm is formed, and a second concave with a diameter of 2R = 11.08 mm, which is larger than the diameter D of the ball 11 = 11.00 mm, is formed on the opening side of the rocker arm recess 12 from the bottom concave spherical surface 13. A spherical surface 14 is formed.
なおロツカーアーム凹部１２の底面側凹球面１
３の中心にはテーパ面１６とオイル供給孔１７が
形成されている。 Note that the concave spherical surface 1 on the bottom side of the Rocker arm recess 12
3, a tapered surface 16 and an oil supply hole 17 are formed in the center.
第３図ないし第５図に図示の実施例は前記した
ように構成されているので、ボール１１は、ロツ
カーアーム凹部１２の底面側における直径2r＝
10.80mmの第１の凹球面１３と、直径2R＝11.08mm
の開口側第２の凹球面１４とが交わる交線１５に
線接触した状態で支持される。 Since the embodiment shown in FIGS. 3 to 5 is constructed as described above, the diameter of the ball 11 on the bottom side of the rocker arm recess 12 is 2r=
First concave spherical surface 13 of 10.80mm and diameter 2R = 11.08mm
It is supported in a state in which it is in line contact with an intersection line 15 where the second concave spherical surface 14 on the opening side intersects.
このように交線１５に沿つた線接触でボール１
１はロツカーアーム凹部１２に支持されるため、
球面対偶１０に大きな押付け力や振動力が働いて
も、ボール１１とロツカーアーム凹部１２との接
触部分の面積を広げて、その単位面積当りの押付
け力を減少させることができ、球面対偶１０の摩
耗を可及的に阻止することができる。 In this way, with line contact along the intersection line 15, the ball 1
1 is supported by the rocker arm recess 12, so
Even if a large pressing force or vibration force acts on the spherical pair 10, the area of contact between the ball 11 and the rocker arm recess 12 can be expanded, and the pressing force per unit area can be reduced, thereby reducing wear on the spherical pair 10. can be prevented as much as possible.
また、ロツカーアーム凹部１２の開口側凹球面
１４を研磨する際に、この研磨時間を短縮すれ
ば、底側第１凹球面１３と開口側第２凹球面１４
とが交わる交線１５を上方に移動させてその接触
角θを増大させ、ボール１１とロツカーアーム凹
部１２との中心軸１８に対し直角に働く力に対し
ボール１１をロツカーアーム凹部１２に安定して
支持させることができる。 In addition, when polishing the opening-side concave spherical surface 14 of the rocker arm recess 12, if this polishing time is shortened, the bottom-side first concave spherical surface 13 and the opening-side second concave spherical surface 14 can be polished.
By moving the intersection line 15 where the two intersect upward to increase the contact angle θ, the ball 11 is stably supported in the rocker arm recess 12 against the force acting perpendicularly to the central axis 18 between the ball 11 and the rocker arm recess 12. can be done.
さらに前記研磨時間を延長すれば、交線１５を
底面側凹球面１３のテーパ面１６に接近させてそ
の接触角θを減少させ、ボール１１とロツカーア
ーム凹部１２とに働く中心軸１８に沿つた力に対
し小さな接触圧力でボール１１をロツカーアーム
凹部１２に支持させることができ、球面対偶１０
の摩耗をできるだけ防ぐことができる。 If the polishing time is further extended, the line of intersection 15 approaches the tapered surface 16 of the concave spherical surface 13 on the bottom side, reducing the contact angle θ, and the force acting on the ball 11 and the rocker arm recess 12 along the central axis 18 increases. The ball 11 can be supported in the rocker arm recess 12 with a small contact pressure compared to the spherical pair 10.
Wear can be prevented as much as possible.
さらにまた機械加工による底面側凹球面１３の
形成後に、浸炭焼入処理を施した際に、これに伴
なつてロツカーアーム凹部１２が歪んでも、研磨
加工により開口側凹球面１４を形成したため、加
工精度が高い。 Furthermore, even if the rocker arm recess 12 is distorted when carburizing and quenching is performed after forming the concave spherical surface 13 on the bottom side by machining, the concave spherical surface 14 on the opening side is formed by polishing, so the machining accuracy is is high.
しかも開口側第２凹球面１４の研磨加工後に、
軟窒化処理を施したため、ボール１１に対する接
触表面の硬度を上げてこの摩耗をさらに少くする
ことができる。 Moreover, after polishing the second concave spherical surface 14 on the opening side,
Since the soft nitriding treatment is performed, the hardness of the contact surface with the ball 11 can be increased to further reduce this wear.
発明の効果
このように本考案においては、前記球面凸部よ
り小さな径の凹球面と該球面凸部より大きな径の
凹球面とが交わる円弧に沿つて該球面凸部を線接
触させることができるため、該球面凸部と凹面受
座との接触面積を広げて接触面圧を低下し、球面
対偶の耐久性を向上させることができる。Effects of the Invention As described above, in the present invention, the spherical convex portion can be brought into line contact along the arc where the concave spherical surface having a smaller diameter than the spherical convex portion and the concave spherical surface having a larger diameter than the spherical convex portion intersect. Therefore, the contact area between the spherical convex portion and the concave seat can be increased, the contact surface pressure can be reduced, and the durability of the spherical pair can be improved.
また前記凹面受座における２種類の凹球面の各
半径とその中心距離とを適宜選定すれば、前記球
面凸部の接触面位置を任意に設定することがで
き、例えば球面対偶の中心軸に沿つた荷重が大き
い場合には、その接触面角を小さくすれば、この
荷重に充分に耐えることができ、逆に球面対偶の
中心軸に対し直角方向の力が加わり、球面凸部が
凹面受座より外れ易い場合には、その接触角を大
きくすれば、凹面受座より球面凸部を外さずこれ
を確固と支持することができる。 Furthermore, by appropriately selecting each radius of the two types of concave spherical surfaces in the concave seat and their center distances, the contact surface position of the spherical convex portion can be arbitrarily set, for example, along the central axis of the spherical pair. If the load is large, reducing the contact surface angle can sufficiently withstand this load. Conversely, a force perpendicular to the center axis of the spherical pair is applied, causing the spherical convex part to meet the concave seat. If it is more likely to come off, by increasing the contact angle, it is possible to firmly support the spherical convex portion without removing it from the concave seat.
しかもこのことは、球面凸部の中心位置を容易
に固定でき結果なり、動弁系に生ずるクリアラン
ス調整および設定を均一かつ最小限に抑制してろ
セツテイングでき、確実な動弁動作を得ることが
できる。 Moreover, this allows the center position of the spherical convex portion to be easily fixed, resulting in clearance adjustment and settings that occur in the valve train system that can be uniformly and minimized for filter setting, resulting in reliable valve train operation. .
さらに本発明では、凹面受座には、まず球面凸
部より半径の小さな凹球面を形成した後、球面凸
部より半径の大きな凹球面を形成し、２種類の径
の異なる球面加工を施すだけで、所望の球面対偶
凹面受座を製造することができるので、工具の管
理と加工が容易で生産コストが安い。 Furthermore, in the present invention, on the concave catch, first a concave spherical surface with a smaller radius than the spherical convex portion is formed, and then a concave spherical surface with a larger radius than the spherical convex portion is formed, and two types of spherical surfaces with different diameters are simply processed. Since the desired spherical and even concave seats can be manufactured, tool management and processing are easy and production costs are low.
第１図および第２図は従来の球面対偶の縦断正
面図、第３図は本発明に係る球面対偶受部の一実
施例を図示した一部縦断側面図、第４図および第
５図はその製作工程を図示した要部拡大縦断正面
図である。
１…自動車用ガソリンエンジン、２…動弁装
置、３…ロツカーアーム、４…オイルタペツト、
５…プツシユロツド、６…カムシヤフト、７…カ
ム、８…吸気弁、９…排気弁、１０…球面対偶、
１１…ボール、１２…ロツカーアーム凹部、１３
…底面側凹球面、１４…開口側凹球面、１５…交
線、１６…テーパ面、１７…オイル供給孔、１８
…中心軸、１９…軸。
1 and 2 are longitudinal sectional front views of a conventional spherical pair, FIG. 3 is a partial longitudinal sectional side view illustrating an embodiment of a spherical pair receiver according to the present invention, and FIGS. 4 and 5 are FIG. 2 is an enlarged vertical sectional front view of the main part illustrating the manufacturing process. DESCRIPTION OF SYMBOLS 1...Automotive gasoline engine, 2...Valve train, 3...Rocker arm, 4...Oil tappet,
5... Push rod, 6... Camshaft, 7... Cam, 8... Intake valve, 9... Exhaust valve, 10... Spherical pair,
11...Ball, 12...Rotzker arm recess, 13
...Concave spherical surface on the bottom side, 14...Concave spherical surface on the opening side, 15...Intersection line, 16...Tapered surface, 17...Oil supply hole, 18
...center axis, 19...axis.
Claims (1)
一部である球面凸部と、該球面凸部を受けてこれ
を支持する凹面受座とよりなる球面対偶におい
て、該凹面受座の一部底面側は、前記球面凸部よ
り径の小さな凹球面に形成され、該底面側の凹球
面より凹面受座の開口側は前記球面凸部より径の
大きな凹球面に形成されたことを特徴とする球面
対偶の凹面受座。1. In a spherical pair consisting of a sphere or at least a spherical convex portion whose contact portion surface is a part of the convex spherical surface, and a concave catch that receives and supports the spherical convex portion, a part of the bottom surface side of the concave catch A spherical surface is formed as a concave spherical surface having a smaller diameter than the spherical convex portion, and a concave spherical surface having a larger diameter than the spherical convex portion is formed on the opening side of the concave catch than the concave spherical surface on the bottom side. Counterpart concave catch.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23133785A JPS62182408A (en) | 1985-10-18 | 1985-10-18 | Spherical contraposition receiving seat |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP23133785A JPS62182408A (en) | 1985-10-18 | 1985-10-18 | Spherical contraposition receiving seat |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS62182408A JPS62182408A (en) | 1987-08-10 |
| JPH0222205B2 true JPH0222205B2 (en) | 1990-05-17 |
Family
ID=16922051
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP23133785A Granted JPS62182408A (en) | 1985-10-18 | 1985-10-18 | Spherical contraposition receiving seat |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS62182408A (en) |
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0650115A (en) * | 1992-07-31 | 1994-02-22 | Mitsubishi Motors Corp | Valve system structure with variable valve timing mechanism |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6447906U (en) * | 1987-09-21 | 1989-03-24 | ||
| JPH11257340A (en) * | 1998-03-11 | 1999-09-21 | Ichikoh Ind Ltd | Ball joint structure |
-
1985
- 1985-10-18 JP JP23133785A patent/JPS62182408A/en active Granted
Cited By (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH0650115A (en) * | 1992-07-31 | 1994-02-22 | Mitsubishi Motors Corp | Valve system structure with variable valve timing mechanism |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS62182408A (en) | 1987-08-10 |
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Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| LAPS | Cancellation because of no payment of annual fees |