JPS631705A - Valve operating timing varying device for engine - Google Patents
Valve operating timing varying device for engineInfo
- Publication number
- JPS631705A JPS631705A JP14276286A JP14276286A JPS631705A JP S631705 A JPS631705 A JP S631705A JP 14276286 A JP14276286 A JP 14276286A JP 14276286 A JP14276286 A JP 14276286A JP S631705 A JPS631705 A JP S631705A
- Authority
- JP
- Japan
- Prior art keywords
- engine
- timing belt
- timing
- eccentric pin
- support shaft
- 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.)
- Pending
Links
- 238000002485 combustion reaction Methods 0.000 description 3
- 230000000694 effects Effects 0.000 description 3
- 229920003002 synthetic resin Polymers 0.000 description 3
- 239000000057 synthetic resin Substances 0.000 description 3
- 238000006243 chemical reaction Methods 0.000 description 2
- 241000894006 Bacteria Species 0.000 description 1
- 235000017166 Bambusa arundinacea Nutrition 0.000 description 1
- 235000017491 Bambusa tulda Nutrition 0.000 description 1
- 241001330002 Bambuseae Species 0.000 description 1
- 235000015334 Phyllostachys viridis Nutrition 0.000 description 1
- 239000011425 bamboo Substances 0.000 description 1
- 238000005452 bending Methods 0.000 description 1
- 230000003111 delayed effect Effects 0.000 description 1
- 238000010586 diagram Methods 0.000 description 1
- 238000005516 engineering process Methods 0.000 description 1
- 230000006870 function Effects 0.000 description 1
- 230000008450 motivation Effects 0.000 description 1
- 239000004575 stone Substances 0.000 description 1
- 238000004804 winding 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
- F01L1/34—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift
- F01L1/344—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear
- F01L1/348—Valve-gear or valve arrangements, e.g. lift-valve gear characterised by the provision of means for changing the timing of the valves without changing the duration of opening and without affecting the magnitude of the valve lift changing the angular relationship between crankshaft and camshaft, e.g. using helicoidal gear by means acting on timing belts or chains
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Valve-Gear Or Valve Arrangements (AREA)
- Valve Device For Special Equipments (AREA)
Abstract
Description
【発明の詳細な説明】
〔産業上の利用分野〕
この発明はクランク軸と吸排2個のカム軸の間に巻回さ
れる調時ベルトの外面を押圧して、吸気弁と排気弁この
作動位相を変化させる弁開閉時期可変装置の改良に関す
るもので、特に、この可変装置をダイヤフラム装置やソ
レノイド装置などの往復駆動手段によって作動させる装
置において、これら往復駆動手段に反力として作用する
ベルトの張力を可及的に軽減させる装置に関する。[Detailed Description of the Invention] [Industrial Application Field] This invention presses the outer surface of a timing belt wound between a crankshaft and two intake and exhaust camshafts to control the operation of the intake valve and exhaust valve. This relates to the improvement of a variable valve timing device that changes the phase, and in particular, in a device in which this variable device is operated by a reciprocating drive means such as a diaphragm device or a solenoid device, the tension of the belt that acts as a reaction force on the reciprocating drive means. The present invention relates to a device that reduces as much as possible.
一般に、4行程エンジンでは、弁の開閉時期を調節する
ために、吸気用と排気用このカム軸を各別に設け、吸気
側に巻回した調時チェーンやベルトの外面を押圧して吸
気用と排気用このカム軸の位相を変化させる装置が提案
されている(例えば実開昭57−92807号公報〕。Generally, in a four-stroke engine, in order to adjust the opening and closing timing of the valves, separate camshafts are provided for intake and exhaust, and pressure is applied to the outer surface of a timing chain or belt wound on the intake side. A device for changing the phase of this exhaust camshaft has been proposed (for example, Japanese Utility Model Application Publication No. 57-92807).
然しなかも、調時チェーン中ベルトを押圧するダイヤフ
ラムやソレノイドあるいは1!動機などを用いている。However, the diaphragm, solenoid, or 1! that presses the belt in the timing chain! It uses motivation, etc.
このため、弁の開閉時期を変更、る場合はもちろん、こ
れを特定の状態に維持するときにも、ベルトからの反力
に対抗するために常時大きな作動力を必要とし、エンジ
ンにとって大きな動力損失を生じる。Therefore, not only when changing the opening and closing timing of the valve, but also when maintaining it in a specific state, a large operating force is constantly required to counteract the reaction force from the belt, resulting in a large power loss for the engine. occurs.
この発明は上記不具合を解消し、カム軸の位相を変化さ
せるとき以外の時期における動力損失を可及的に低減す
ることを目的とするもので、クランク軸から調時ベルト
を介して駆動される吸気カム軸と排気カム軸を備え、そ
れらの一方のカム軸に巻回された調時ベルトの外面へ揺
動腕に支持したコーラを押圧すると共に、この揺動腕に
設けた長孔とこれに係合した偏芯ピンを持つ支軸とから
なる偏芯カム機構を設け、その支軸を作動手段に連動す
る作動軸に連結すると共に、少なくとも揺動腕が一側と
他側の揺動限度1で揺動したとき、前記偏芯ピンとその
支軸の軸線がほぼ揺動腕の揺動中心を軸とする円の上に
位置するよう設定された点に特徴がある。The purpose of this invention is to eliminate the above-mentioned problems and reduce power loss as much as possible at times other than when changing the phase of the camshaft. It is equipped with an intake camshaft and an exhaust camshaft, and presses a cola supported by a swinging arm onto the outer surface of a timing belt wound around one of the camshafts. An eccentric cam mechanism is provided, which includes a support shaft having an eccentric pin engaged with the support shaft, and the support shaft is connected to an actuation shaft that is linked to an actuation means, and at least the swinging arm swings on one side and the other side. The device is characterized in that when the device swings at limit 1, the axes of the eccentric pin and its support shaft are set to lie approximately on a circle centered around the center of swing of the swing arm.
少なくとも揺動腕が揺動の限度位置にあるときは、−時
プーリを介して揺動腕に作用する調時ベルトの張力は、
偏芯ピンとその支軸の配列方向に作用するから、偏芯ピ
ンにはこれを作動する力に抗する力は作用しない。At least when the swinging arm is at its swinging limit position, the tension of the timing belt acting on the swinging arm via the pulley is:
Since the force acts in the direction in which the eccentric pins and their support shafts are arranged, no force acts on the eccentric pins to resist the force that operates them.
〔5A施例〕
以下、図示の実施例によってこの発明を説明すると、第
2図中、1は■形6気筒エンジンで、3個ずつの気筒を
有する2個のシリンダ列R1Lが設けられている。気筒
はシリンダブロック2に形成されたシリンダ孔2aと、
その上面を覆うシリンダヘッド3およびシリンダ孔2a
へ嵌合したピストン4とからなる燃焼室5を含む。6は
クランク軸、7はコンロッドである。[Embodiment 5A] Hereinafter, the present invention will be explained with reference to the illustrated embodiment. In Fig. 2, 1 is a ■-shaped six-cylinder engine, and two cylinder rows R1L each having three cylinders are provided. . The cylinder has a cylinder hole 2a formed in the cylinder block 2,
Cylinder head 3 and cylinder hole 2a covering its upper surface
It includes a combustion chamber 5 consisting of a piston 4 fitted into the combustion chamber 5. 6 is a crankshaft, and 7 is a connecting rod.
■バンクの内側には吸気通路8が、外側には排気通路9
が開口しており、それぞれ吸気弁8aと排気弁9a を
介して燃焼室5へ接続されている。■Intake passage 8 is on the inside of the bank, and exhaust passage 9 is on the outside.
are open and connected to the combustion chamber 5 via an intake valve 8a and an exhaust valve 9a, respectively.
11は吸気弁8aを開閉する吸気カム軸、12は排気弁
9a を開閉する排気カム軸である。11 is an intake camshaft that opens and closes the intake valve 8a, and 12 is an exhaust camshaft that opens and closes the exhaust valve 9a.
吸気カム軸11と排気カム軸12の駆動系を、第1図で
示す。各軸11.12は吸気カム歯車13と排気カム歯
車14が取付けられ、それらとクランク軸6に取付けた
調時歯車15この間には調時ベルト16が巻回されてい
る。なお、調時ベルト16はこの例では歯付きベルトが
示されているが、チェーンでも代替できることは勿論で
ある。また、調時歯車15の外方の矢印はクランク軸6
の回転方向を示す。A drive system for the intake camshaft 11 and the exhaust camshaft 12 is shown in FIG. An intake cam gear 13 and an exhaust cam gear 14 are attached to each shaft 11, 12, and a timing belt 16 is wound between them and a timing gear 15 attached to the crankshaft 6. Although a toothed belt is shown as the timing belt 16 in this example, it goes without saying that a chain may be used instead. Also, the arrow on the outside of the timing gear 15 indicates the crankshaft 6.
indicates the direction of rotation.
この発明において、調時ベルト16は吸気カム歯車13
と排気カム歯車14この間を通してクランク軸6側へ引
込まれ、そこに設けたローラ17へ巻回しである。18
a はアイドルローラである。In this invention, the timing belt 16 is connected to the intake cam gear 13.
The exhaust cam gear 14 is drawn into the crankshaft 6 side through the space between the exhaust cam gear 14 and wound around a roller 17 provided there. 18
a is an idle roller.
ローラ17は第7図、第8図で示すように、揺動腕18
から突出する支@ 17 a にボール17bを介して
回転可能に軸支されている。揺動腕18はシリンダブロ
ック2へ支持したカラー19と球軸受20とを介してボ
ルト21によシ揺動可能に支持され、且つローラ1Tの
近傍に設けた2個の案内孔22とそこに設けた他のボル
ト23によシ、ベルト16の張力による曲がシを防止し
ている。The roller 17 is connected to the swinging arm 18 as shown in FIGS. 7 and 8.
It is rotatably supported via a ball 17b by a support @17a protruding from the support. The swinging arm 18 is swingably supported by a bolt 21 via a collar 19 supported on the cylinder block 2 and a ball bearing 20, and is connected to two guide holes 22 provided near the roller 1T. The other bolt 23 provided prevents bending due to the tension of the belt 16.
すなわち、ボルト23はシリンダブロック2に設けた取
付座24上へ、硬質合成樹脂製の鍔付きカラー25と硬
質合成樹脂製のワッシャ26を通して螺着され、カラー
25は前記案内孔22へ摺動のみ可能に精密に嵌合され
ている。That is, the bolt 23 is screwed onto the mounting seat 24 provided on the cylinder block 2 through a flanged collar 25 made of hard synthetic resin and a washer 26 made of hard synthetic resin, and the collar 25 only slides into the guide hole 22. The fit is as precise as possible.
揺動腕18は作動装置によって作動される。この実施例
において作動装置はダイヤフラム装置31と偏芯カム機
構Cとからなり、ロッド32を介して連結され°た弧状
歯車33と、この弧状歯車33に噛合するビニオン34
とを含む。ピニオン34は支軸Sによって軸支されると
共に、その−端面に偏芯ピン35が設けてあシ、前記支
軸Sは偏芯ピン35の支軸Sとしても機能する。偏芯ピ
ン35と揺動腕18この連結は長孔36と、これに摺動
可能に嵌合された硬質合成樹脂製のスライダ3Tで構成
され、これに設けた孔37a に前記偏芯ピン35が遊
合している。このように長孔36と偏芯ピン35および
ビニオン34によって偏芯カム。The swinging arm 18 is actuated by an actuating device. In this embodiment, the actuating device consists of a diaphragm device 31 and an eccentric cam mechanism C, including an arcuate gear 33 connected via a rod 32, and a pinion 34 meshing with the arcuate gear 33.
including. The pinion 34 is supported by a support shaft S, and an eccentric pin 35 is provided on the opposite end surface of the pinion 34, and the support shaft S also functions as the support shaft S of the eccentric pin 35. This connection between the eccentric pin 35 and the swinging arm 18 is made up of a long hole 36 and a hard synthetic resin slider 3T slidably fitted into the long hole 36, and the eccentric pin 35 is inserted into the hole 37a provided in this. are playing together. In this way, the long hole 36, the eccentric pin 35, and the pinion 34 form an eccentric cam.
機構Cが構成される。Mechanism C is configured.
なお、ダイヤフラム装[31は吸気負圧を作動源として
、クランク軸60回転速度を信号とするコンピュータ(
図示しない)によって動作される。In addition, the diaphragm device [31 is a computer (
(not shown).
作動装置としては、ダイヤプラム装置31に@らず、電
動機Mを用いることも可能である。この例を第6図で示
す。As the actuating device, it is also possible to use an electric motor M instead of the diaphragm device 31. An example of this is shown in FIG.
次にこの動弁機構の作動を説明すると、エンジンが始動
し、クランク軸6が矢印方向へ回転すると、それに伴っ
て調時ベルト16とこれに駆動される各歯車13.14
が同方向へ回転する。Next, to explain the operation of this valve mechanism, when the engine starts and the crankshaft 6 rotates in the direction of the arrow, the timing belt 16 and the gears 13 and 14 driven by it
rotate in the same direction.
エンジンが第9図中、■で示す低速低負荷域で運転され
ると、ダイヤフラム装置31がロッド32を途中まで押
し、弧状歯車33が時計方向へ、またビニオン34が反
時計方向へ回動して、第3図で示すように、(il、i
!#ピン35が図中上方へ移動する結果、偏芯ピン35
とその支軸Sの軸芯が、揺動腕1Bの揺動中心を軸とす
る円Aの上に並び、揺動腕18が反時計方向へ限度まで
揺動丁b0このようにして、右7リンダ列Rのローラ1
7の緊張が弛められる反面、左シリンダ列りのローラ1
Tを緊張させるので、両ローラ17間の調時ベルト16
は右シリンダ列R側のローラ1Tから左シリンダ列りの
ローラ17へ向けて相対的に移動し、各吸気カム歯車1
3.13を反時計方向へ回転させる。その結果、吸気弁
8aの開弁時期を遅らせ、吸気弁8aと排気弁91この
オーバーラツプ期間を短縮する。When the engine is operated in the low speed and low load range indicated by ■ in FIG. 9, the diaphragm device 31 pushes the rod 32 halfway, the arc gear 33 rotates clockwise, and the pinion 34 rotates counterclockwise. As shown in Fig. 3, (il, i
! #As a result of the pin 35 moving upward in the figure, the eccentric pin 35
The axis of the support shaft S is aligned on the circle A with the center of swing of the swing arm 1B as the axis, and the swing arm 18 swings counterclockwise to the limit as far as possible. 7 Roller 1 of cylinder row R
While the tension of roller 7 is relaxed, roller 1 of the left cylinder row
T tension is applied to the timing belt 16 between both rollers 17.
moves relatively from the roller 1T on the right cylinder row R side toward the roller 17 on the left cylinder row, and each intake cam gear 1
3. Rotate 13 counterclockwise. As a result, the opening timing of the intake valve 8a is delayed, and the overlapping period between the intake valve 8a and the exhaust valve 91 is shortened.
また、エンジンが第9図中、■で示される高負荷高速域
で運転され\ば、ダイヤフラム装置31がロッド32を
一層押し出し、弧状歯]$33が一層時計方向へ、また
ピニオン34が反時計方向へ回動して、第4図で示すよ
うに、偏芯ピン35がスライダ37を長孔36の左端部
へ押し付ける結果、それ以上の回動が阻止される。この
結果、揺動腕18が調時ベルト16の張力を受けて、時
計方向へ回動するのが阻止される。したがって、左シリ
ンダ列りのローラITの緊張を弛める反面、右シリンダ
列Rのローラ17では緊張が増す結果、菌付きベルト1
8は左シリンダ列りのローラ17から右シリンダ列Rの
ローラ17へ相対的に移動して各吸気カム歯車13.1
3を時計方向へ回転させ、吸気弁の開閉時期を進角させ
る、すなわち、開閉時期を早くしてオーバーラツプ期間
を拡大する。Furthermore, when the engine is operated in the high-load, high-speed range shown by ■ in FIG. As a result of the eccentric pin 35 pressing the slider 37 against the left end of the elongated hole 36, as shown in FIG. 4, further rotation is prevented. As a result, the swing arm 18 is prevented from rotating clockwise under the tension of the timing belt 16. Therefore, while the tension on the rollers IT in the left cylinder row is relaxed, the tension on the rollers 17 in the right cylinder row R increases, and as a result, the bacteria-containing belt 1
8 relatively moves from the roller 17 of the left cylinder row to the roller 17 of the right cylinder row R, and each intake cam gear 13.1
3 clockwise to advance the opening/closing timing of the intake valve, that is, to advance the opening/closing timing and expand the overlap period.
更に、エンジンが第9図中、1で示す中低速高負荷域で
運転され\ば、ダイヤフラム装置31がロッド32を逆
方向へ極限まで引き、弧状歯車33が反時計方向へ、ま
たピニオン34が時計方向へ回動して、第5図で示すよ
うに、i芯ピン35が図中下方へ移動する結果、偏芯ピ
ン35とその支軸Sの軸芯が、揺動腕18の揺動中心を
軸とする円の上に並ぶ。その結果、揺動腕18が時計方
向へ限度まで揺動する。したがって、左シリンダ列乙の
ローラ17の緊張を弛める反面、石シリンダ列Rのロー
ラ1Tでは緊張を強め、調時ベルト16は左シリンダ列
りのローラ17から右シリンダ列Rのローラ17へ相対
的に移動して各吸気カム歯車13.13を時計方向へ回
転させ、吸気弁の開閉時期を進角させる、よって開閉時
期が早tBオーバーラツプ期間を拡大する。Furthermore, when the engine is operated in the medium-low-speed, high-load region indicated by 1 in FIG. As a result of rotating clockwise and moving the i-core pin 35 downward in the figure as shown in FIG. Arranged in a circle with the center as the axis. As a result, the swinging arm 18 swings clockwise to its limit. Therefore, while the tension of the rollers 17 of the left cylinder row B is relaxed, the tension of the rollers 1T of the stone cylinder row R is increased, and the timing belt 16 is moved from the rollers 17 of the left cylinder row to the rollers 17 of the right cylinder row R. , and rotates each intake cam gear 13, 13 clockwise to advance the opening/closing timing of the intake valve, thereby expanding the early tB overlap period.
この発明は以上のように、クランク軸から調時ベルトを
介して駆動される吸気カム軸と排気カム軸を備え、それ
らの一方のカム軸に巻回された調時ベルト16の外面へ
揺動腕18に支持し九ローラ17を押圧すると共に、そ
の揺動腕に設けた長孔36とこれに保合した偏芯ピン3
5を持つ支軸Sとからなる偏芯カム機構Cを設け、その
支軸Sを作動手段30に連結すると共に、前記偏芯ピン
35とその支軸Sの軸線を、少なくとも揺動腕が一側と
他側の揺動限度まで揺動したとき、前記偏芯ピン35と
その支軸Sの軸線がほぼ揺動腕の揺動中心を軸とする円
Aの上に位置するよう設定したものである。したがって
、a−′う17を介して揺動腕18に作用する調時ベル
ト16の張力は、揺動腕1Bが揺動してその限度位置に
あるときは、偏芯ピン35とその支軸Sが揺動腕18の
揺動中心を軸とする円Aの接線上に並ぶ。よって、この
状態な定常状態として使用すれば、吸気弁の開閉時期を
所定の時期に維持するとき、作動装置30は調時ベルト
の張力に対抗する必要がなく、常時は大きな作動力を必
要とせず、エンジンの動力損失を減少させることができ
る効果がある。As described above, this invention includes an intake camshaft and an exhaust camshaft that are driven from a crankshaft via a timing belt, and the timing belt 16, which is wound around one of the camshafts, swings toward the outer surface of the timing belt 16. It is supported by the arm 18 and presses the nine rollers 17, and an elongated hole 36 provided in the swinging arm and an eccentric pin 3 held therein.
An eccentric cam mechanism C consisting of a support shaft S with The axis of the eccentric pin 35 and its support shaft S is set so that when the swing arm swings to the swing limit on both sides, the axis of the eccentric pin 35 and its support shaft S is located approximately on a circle A centered on the swing center of the swing arm. It is. Therefore, when the swinging arm 1B swings and is at its limit position, the tension of the timing belt 16 acting on the swinging arm 18 through the a-' S is lined up on a tangent to a circle A whose axis is the center of swing of the swing arm 18. Therefore, if used in this steady state, the actuating device 30 does not need to resist the tension of the timing belt when maintaining the opening/closing timing of the intake valve at a predetermined timing, and does not require a large actuating force at all times. First, it has the effect of reducing engine power loss.
図面はこの発明の実施例を示すもので、第111は調時
ベルトの巻回状態を示すエンジンの正面図、g2図はエ
ンジンの断面図、第3図がら第5図1では第2図中の要
部の拡大正面図、第6図は他の実施例を示す要部の竹視
図、第7図は第1@中の■−■断面図、第8図は第1図
中の■−■断面図、第9図は作動特性図である。
11・・・俸吸気カム軸、12・・・・排気カム軸、1
6・・・・調時ベルト、18@・・・揺動腕、33・・
−一弧状歯車、3411・・・ピニオン、35・・・・
偏芯ピン、3611・・・長孔。The drawings show an embodiment of the present invention, in which reference numeral 111 is a front view of the engine showing the winding state of the timing belt, drawing g2 is a cross-sectional view of the engine, and drawings 3 and 5 are shown in FIG. Fig. 6 is a bamboo perspective view of the main part showing another embodiment, Fig. 7 is a sectional view taken along ■-■ in Fig. 1, and Fig. 8 is a cross-sectional view taken along ■-■ in Fig. 1. -■ sectional view and FIG. 9 are operating characteristic diagrams. 11... Salary intake camshaft, 12... Exhaust camshaft, 1
6... Timing belt, 18@... Rocking arm, 33...
- Single arc gear, 3411...Pinion, 35...
Eccentric pin, 3611...long hole.
Claims (5)
気カム軸と排気カム軸を備え、それらの一方のカム軸に
巻回された調時ベルトの外面へ揺動腕に支持したローラ
を押圧すると共に、この揺動腕に設けた長孔とこれに係
合した偏芯ピンを持つ支軸とからなる偏芯カム機構を設
け、その支軸を作動手段に連動する作動軸に連結すると
共に、少なくとも揺動腕が一側と他側の揺動限度まで揺
動したとき、前記偏芯ピンとその支軸の軸線がほぼ揺動
腕の揺動中心を軸とする円の上に位置するよう設定され
たエンジンの弁開閉時期可変装置。(1) An intake camshaft and an exhaust camshaft are driven from the crankshaft via a timing belt, and a roller supported by a swinging arm is attached to the outer surface of the timing belt wound around one of the camshafts. At the same time as pressing, an eccentric cam mechanism consisting of a long hole provided in this swinging arm and a support shaft having an eccentric pin engaged with the long hole is provided, and the support shaft is connected to an operating shaft that is interlocked with the operating means. At the same time, when the swinging arm swings at least to the swinging limits on one side and the other side, the axis of the eccentric pin and its supporting shaft is located approximately on a circle centered around the swinging center of the swinging arm. An engine valve opening/closing timing variable device set as follows.
第1項記載のエンジンの弁開閉時期可変装置。(2) The variable valve opening/closing timing device for an engine according to claim 1, wherein the timing belt is a toothed belt.
項記載のエンジンの弁開閉時期可変装置。(3) Claim 1 that the timing belt is a chain
The valve opening/closing timing variable device for the engine as described in .
範囲第1項記載のエンジンの弁開閉時期可変装置。(4) The variable valve opening/closing timing device for an engine according to claim 1, wherein the reciprocating drive means is an electromagnetic solenoid.
囲第1項記載のエンジンの弁開閉時期可変装置。(5) The variable valve timing device for an engine according to claim 1, wherein the reciprocating drive means is a diaphragm.
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP14276286A JPS631705A (en) | 1986-06-20 | 1986-06-20 | Valve operating timing varying device for engine |
US07/047,053 US4726331A (en) | 1986-05-06 | 1987-05-06 | Means for variable valve timing for engine |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
JP14276286A JPS631705A (en) | 1986-06-20 | 1986-06-20 | Valve operating timing varying device for engine |
Publications (1)
Publication Number | Publication Date |
---|---|
JPS631705A true JPS631705A (en) | 1988-01-06 |
Family
ID=15322988
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
JP14276286A Pending JPS631705A (en) | 1986-05-06 | 1986-06-20 | Valve operating timing varying device for engine |
Country Status (1)
Country | Link |
---|---|
JP (1) | JPS631705A (en) |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008010225A1 (en) | 2007-02-23 | 2008-08-28 | Honda Motor Co., Ltd. | Variable valve timing mechanism |
CN108825322A (en) * | 2018-09-06 | 2018-11-16 | 广西玉柴机器股份有限公司 | The timing phase system of engine |
-
1986
- 1986-06-20 JP JP14276286A patent/JPS631705A/en active Pending
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
DE102008010225A1 (en) | 2007-02-23 | 2008-08-28 | Honda Motor Co., Ltd. | Variable valve timing mechanism |
CN108825322A (en) * | 2018-09-06 | 2018-11-16 | 广西玉柴机器股份有限公司 | The timing phase system of engine |
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