JPS5912161A - Controller for ignition timing of engine - Google Patents
Controller for ignition timing of engineInfo
- Publication number
- JPS5912161A JPS5912161A JP12340182A JP12340182A JPS5912161A JP S5912161 A JPS5912161 A JP S5912161A JP 12340182 A JP12340182 A JP 12340182A JP 12340182 A JP12340182 A JP 12340182A JP S5912161 A JPS5912161 A JP S5912161A
- Authority
- JP
- Japan
- Prior art keywords
- rotating shaft
- ignition timing
- engine
- drive member
- fixed
- 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.)
- Granted
Links
Classifications
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
- F02P7/00—Arrangements of distributors, circuit-makers or -breakers, e.g. of distributor and circuit-breaker combinations or pick-up devices
- F02P7/10—Drives of distributors or of circuit-makers or -breakers
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F02—COMBUSTION ENGINES; HOT-GAS OR COMBUSTION-PRODUCT ENGINE PLANTS
- F02P—IGNITION, OTHER THAN COMPRESSION IGNITION, FOR INTERNAL-COMBUSTION ENGINES; TESTING OF IGNITION TIMING IN COMPRESSION-IGNITION ENGINES
- F02P5/00—Advancing or retarding ignition; Control therefor
- F02P5/04—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions
- F02P5/05—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means
- F02P5/10—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means dependent on fluid pressure in engine, e.g. combustion-air pressure
- F02P5/103—Advancing or retarding ignition; Control therefor automatically, as a function of the working conditions of the engine or vehicle or of the atmospheric conditions using mechanical means dependent on fluid pressure in engine, e.g. combustion-air pressure dependent on the combustion-air pressure in engine
Abstract
Description
【発明の詳細な説明】
この発明は機関の点火時期を、機関の回転数に対応して
制御する機関点火時期制御装置の改良に関するものであ
る。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an improvement in an engine ignition timing control device that controls the ignition timing of an engine in accordance with the rotational speed of the engine.
従来一般に知られているこの種の機関点火時期制御装置
を第１図乃至第３図により説明する。図において、（１
）は機関（図示せず、以下同じ）に固定されるハクジン
グ、（２）はこのハクジング（１）に圧入された軸受メ
タル、（３）はこの軸受メタル（２）に回動自在に支承
され機関により駆動される回転軸、ガ
（４）は上記回転軸に固定された多バナプレート、 （
５）はこのガバナプレート（４）に立設された一対のビ
ン、（６）はこのピン（５）に遊嵌された一対のガバナ
クエイ）、（７）ｆｄ上記ガバナプレート（４）に固定
されたばね掛け、（８）は上記ガバナウェイト（６）と
上記ばね掛け（７）との間に張架されたスプリング、（
９）は上記ガバナウェイト（６）の反ガバナプレート（
４）側に突設されたピン、（１０）はこのピン（９）が
遊嵌される長穴部（１０ａ） を有し、後述するカム
（１１）の第１図中下端に固定されるカムベース、（１
１） ｒ／′ｉ上記回転軸（３）に回動自在に遊嵌され
た筒状のカム、（１２）は上記回転軸（３）の第１図中
上端にねじ（１３）によって固定され、上記カム（１１
）の軸方向の揺動を阻止するワッシャ、（１４）は上記
カム（１１）を囲んで略円板状に形成され上記ハウジン
グ（１）に固定された固定プレート、（１５）はこの固
定プレート（１４）に回動自在に支承された可動プレー
ト、（１６）ｌ−ｔこの可動プレート（１５）に装着さ
れ、点火時期決定部材を構成する従来周知の断続器で、
上記カム（１１）の回動によって接点（１６ａ）が開閉
し、点火コイル（図示せず）の−次電流を断続するもの
である。（１７）は上記ハクジ午
ング（１）の一端開口部を閉塞する配電雲ヤツプである
。DESCRIPTION OF THE PREFERRED EMBODIMENTS This type of engine ignition timing control device, which has been generally known in the past, will be explained with reference to FIGS. 1 to 3. In the figure, (1
) is a housing fixed to the engine (not shown, the same applies hereinafter), (2) is a bearing metal press-fitted into this housing (1), and (3) is rotatably supported by this bearing metal (2). The rotary shaft driven by the engine (4) is a multi-banner plate fixed to the rotary shaft, (
5) is a pair of bottles erected on this governor plate (4), (6) is a pair of governor pins loosely fitted on this pin (5), and (7) fd is fixed on the governor plate (4). The spring hook (8) is a spring stretched between the governor weight (6) and the spring hook (7).
9) is the anti-governor plate (
4) The pin (10) protruding from the side has an elongated hole (10a) into which the pin (9) is loosely fitted, and is fixed to the lower end of the cam (11) in Fig. 1, which will be described later. Cam base, (1
1) r/'i A cylindrical cam (12) is rotatably loosely fitted to the rotating shaft (3), and is fixed to the upper end of the rotating shaft (3) in FIG. 1 by a screw (13). , the above cam (11
), (14) is a fixing plate formed in a substantially disc shape surrounding the cam (11) and fixed to the housing (1), and (15) is this fixing plate. A movable plate rotatably supported by (14), (16) a conventional interrupter which is attached to this movable plate (15) and constitutes an ignition timing determining member;
The contact (16a) is opened and closed by the rotation of the cam (11), and the secondary current of the ignition coil (not shown) is interrupted. (17) is a power distribution cloud that closes one end opening of the above-mentioned hatch (1).
上記のように構成されたものにおいて、機関により回転
軸（３）が回転されると、カム（１１）がガバナプＶ−
ト（４）、ピン（５）、ガバナウェイト（６）、スプリ
ング（８）、ピン（９）、及びカムベース（１０）を介
して回転されるため、断続器（１６）の接点（１６ａ）
が開閉し、イグニションコイル（図示せず）の−次電流
が断続される。ここで、機関の回転数に応じた点火時期
の制御動作について説明すると、機関の回転速度が所定
値以下の場合、ガバナウェイト（６）がスプリング（８
）によって付勢されているため、カムベース（１０）の
位置、即ちカム（１１）の位置は第３図（Ａ）の位置に
ある。次に、機関の回転速度が上昇すると、回転速度に
応じてガバナウェイト（６）の遠心力が増大するため、
ガバナウェイト（６）は、スプリング（８）の張力に抗
してガバナウェイト（６）の遠心力とスプリング（８）
の張力とがつり合う位置まで飛開する。In the device configured as described above, when the rotating shaft (3) is rotated by the engine, the cam (11)
The contact (16a) of the interrupter (16)
opens and closes, and the secondary current of the ignition coil (not shown) is interrupted. Here, to explain the control operation of the ignition timing according to the engine speed, when the engine speed is below a predetermined value, the governor weight (6) is activated by the spring (8).
), the position of the cam base (10), that is, the position of the cam (11) is at the position shown in FIG. 3(A). Next, as the rotational speed of the engine increases, the centrifugal force of the governor weight (6) increases according to the rotational speed.
The governor weight (6) resists the tension of the spring (8), and the centrifugal force of the governor weight (6) and the spring (8)
fly to a position where the tension is balanced.
このため、カム（１１）は第３図ＣＢ）に示すように、
回転軸（３） Ｋ対して相対的に回動するため、例えば
回転軸（３）の回転方向がＡ矢の方向とすると、断続器
（１６）の開閉動作は第３図（Ａ）のように位置されて
いる場合よりも進角することになる。Therefore, the cam (11), as shown in Figure 3 CB),
Since the rotating shaft (3) rotates relative to K, for example, if the rotating direction of the rotating shaft (3) is in the direction of arrow A, the opening/closing operation of the interrupter (16) will be as shown in Figure 3 (A). The angle will be more advanced than if it were located at .
ところで、機関は、爆発、排気、吸気、圧縮の４行程の
繰り返しにより連続的に運転されるのであるが、排気、
吸気、圧縮の３行程においては爆発時の大きなエネルギ
を受けてその慣性によって駆動されているため、例えば
圧縮行程と爆発行程とでは角加速度が大幅に異なること
になる。この結果、機関に連結された回転軸（３）に訃
いても、機関と同様に急激に角加速度が変動し、更にガ
バナウェイト（８）、カム（１１）等の進角機構の慣性
作用により進角特性が極めて不安定となり、また一方で
は、進角機構が回転体により構成されているため、回転
振動により軸受部、摺動部等が摩耗しやすく耐久性がな
いという欠点があった。By the way, an engine is operated continuously by repeating four strokes: explosion, exhaust, intake, and compression.
In the three strokes of intake and compression, the engine receives large energy from the explosion and is driven by its inertia, so the angular acceleration will be significantly different between the compression stroke and the explosion stroke, for example. As a result, even if the rotating shaft (3) connected to the engine fails, the angular acceleration will fluctuate rapidly just like the engine, and due to the inertia of the advance mechanism such as the governor weight (8) and cam (11). The advance angle characteristics become extremely unstable, and on the other hand, since the advance angle mechanism is constituted by a rotating body, there is a drawback that the bearing section, sliding section, etc. are easily worn out due to rotational vibration, resulting in lack of durability.
この考案は上記のような従来装置の欠点を除去するため
になされたもので、安定した進角特性が得られ、かつ、
耐久性の優れた機関点火時期制御装置を提供することを
目的としている。This invention was made in order to eliminate the drawbacks of the conventional device as described above, and it provides stable advance angle characteristics, and
The purpose is to provide an engine ignition timing control device with excellent durability.
以下、第４図乃至第８図によりこの考案の一実施例を説
明する。図において、（１１）は回転軸（３）に固定さ
れたカム、（１４）は従来と同様に円板状に形成された
固定プレートで、内周にはベアリング（１４ａ）を有し
ている。（１５ａ）は可動プレート（１５）に設けられ
た円弧状の長孔部、（１８）ｌｄ回転軸（３）に固着さ
れた円柱状のドライブメンバ、（１８ａ）ｔｊ：このド
ライブメンバ（１８）の外周附近に内設された永久磁石
で外周にＮ極とＳ極が交互に位置するよう複数配置され
、後述する導体（１９ａ）と鎖交する磁束を発生する。An embodiment of this invention will be described below with reference to FIGS. 4 to 8. In the figure, (11) is a cam fixed to the rotating shaft (3), and (14) is a fixed plate formed in a disk shape as in the conventional case, and has a bearing (14a) on the inner periphery. . (15a) is an arcuate long hole provided in the movable plate (15), (18) is a cylindrical drive member fixed to the ld rotating shaft (3), (18a) tj: this drive member (18) A plurality of permanent magnets are installed near the outer periphery of the permanent magnet, and a plurality of permanent magnets are arranged so that N poles and S poles are alternately located on the outer periphery, and generate magnetic flux that interlinks with a conductor (19a) to be described later.
（１９）は一端の直径が他端の直径よりも大径に形成さ
れた２段円筒形状の磁性体より成るドリグンメンバで、
一端側円筒部で上記ドライブメンバ（１８）を空隙を介
して包囲し、他端側円筒部内周に嵌着されたベアリング
（２０）を介して回転軸（１）に回動自在に支承されて
いる。（１９ａ）は上記ドリグンメンバ（１９）の一端
側円筒部内周に内設された導体、なお、上記ドライブメ
ンバ（２０）と上記ドリグンメンバ（２１）とですべり
連結手段を構成している。(19) is a driven member made of a two-step cylindrical magnetic material with one end having a larger diameter than the other end.
The cylindrical part on one end surrounds the drive member (18) via a gap, and is rotatably supported on the rotating shaft (1) via a bearing (20) fitted on the inner periphery of the cylindrical part on the other end. There is. (19a) is a conductor provided inside the inner periphery of the cylindrical portion at one end of the driven member (19), and the driven member (20) and the driven member (21) constitute a sliding connection means.
（２１）は上記ドリグンメンバ（１９）の他端に固定す
れた外ギヤ、（２２） Ｖｉ固定プレート（１４）に固
定されたギヤ軸、（２３）はこのギヤ軸（２２）に遊嵌
されたギャで上記外ギヤ（２１）と歯合している。（２
４）は一端外周に上記可動プレー） （１５）を固着し
、上記ベアリング（１４ａ）に嵌着され、回動自在に支
持された内ギヤで、上記ギヤ（２３）と歯合している。(21) is an external gear fixed to the other end of the driven member (19), (22) is a gear shaft fixed to the Vi fixing plate (14), and (23) is loosely fitted to this gear shaft (22). The gear meshes with the outer gear (21). (2
4) is an inner gear having the movable play (15) fixed to the outer periphery of one end thereof, fitted in the bearing (14a) and rotatably supported, and meshing with the gear (23).
なお、上記外ギヤ（２１）とギヤ（２３）と内ギヤ（２
４）とで回動手段を構成している。（２５）は上記固定
プレー１− （１４）に立設されたスピンドルで、上記
長孔部（１５ａ）に貫挿されている。（２６）は上記可
動プレート（１５）に立設されたばね掛け、（２７）は
上記スピンドル（２５）と上記ばね掛け（２６）との間
に張架されたスプリングである。その他の符号の説明は
従来装置の説明と同様につき省略する。In addition, the above-mentioned outer gear (21), gear (23), and inner gear (2)
4) constitute a rotating means. (25) is a spindle erected on the fixed play 1-(14), and is inserted through the elongated hole (15a). (26) is a spring hook erected on the movable plate (15), and (27) is a spring stretched between the spindle (25) and the spring hook (26). Descriptions of other symbols are omitted as they are the same as those of the conventional device.
上記のように構成されたものにおいて、機関の回転数に
応じた点火時期の制御動作について説明する。機関によ
り回転軸（３）が回転され、ドライブメンバ（１８）と
ドリグンメンバ（１９）とが相対的に回動すると導体（
１９）の鎖交磁束が変化し、電磁誘導作用により導体（
１９ａ）に二次電流（１）が発生する。この二次電流（
１）による磁界と永久磁石（１８１Ｌ）による磁界との
電磁作用によりドリグンメンバ（１９）にトルクが伝達
され、このトルクは、外ギヤ（２１） 、ギヤ（２３）
及び内ギヤ（２４）にそれぞれ第６図中矢印の方向に伝
達され、可動グレート（１５）には、回転軸（３）の回
転方向、即ち、カム（１１）の回転方向とは逆方向に伝
達される。ここで、可動グレート（１５）に伝達される
トスクはドライブメンバ（１８）とドリグンメンバ（１
９）との相対回転速度、即ち、回転軸（３）の回転速度
に応じて増加するが、まず、回転軸（３）の回転速度が
所定値以下の場合、可動プレー） （１５）の位置、即
ち、断続器（１６）の位置はスプリング（２７）の張力
により第５図に示す位置にある。次に、機関の回転速度
が上昇すると、上述のように可動プレー） （１５）に
伝達されるトルクも上昇し、可動プレー） （１５）、
即ち、断続器（１６）はスプリング（２７）の張力に抗
して、カム（１１）の回転方向とは逆方向に回動され、
点火時期が進角することになる。In the apparatus configured as described above, the ignition timing control operation according to the engine speed will be explained. When the rotary shaft (3) is rotated by the engine and the drive member (18) and the driven member (19) rotate relative to each other, the conductor (
19) changes in the magnetic flux linkage of the conductor (
A secondary current (1) is generated at 19a). This secondary current (
Torque is transmitted to the driven member (19) by the electromagnetic action of the magnetic field generated by 1) and the magnetic field generated by the permanent magnet (181L), and this torque is transmitted to the outer gear (21) and the gear (23).
and the inner gear (24) in the direction of the arrow in FIG. communicated. Here, the task transmitted to the movable grate (15) is the drive member (18) and the driven member (1
9), that is, the rotation speed of the rotating shaft (3), but first, if the rotating speed of the rotating shaft (3) is below a predetermined value, the position of the movable play (15) increases. That is, the interrupter (16) is in the position shown in FIG. 5 due to the tension of the spring (27). Next, as the rotational speed of the engine increases, the torque transmitted to the movable play (15) also increases, as described above, and the
That is, the interrupter (16) is rotated in a direction opposite to the direction of rotation of the cam (11) against the tension of the spring (27),
The ignition timing will be advanced.
なお、この場合の最大進角量はスピンドル（２５）が長
孔部（１５ａ）に当接することにより決定される。また
、上記のように可動プレー） （１５）に伝達されるト
ルクは、回転軸（３）の回転速度で決定されるが、従来
装置と同様に回転軸（３）の角加速度は急激に変動する
。ところが、回転軸（３）に固着されたドライブメンバ
（１８）の角加速度が、回転軸（３）と同様に急激に変
動しても、ドリグンメンバ（１９）はその慣性により、
ドライブメンバ（１８）の急激な角加速度変動に追随せ
ず、安定したトルクを発生する。Note that the maximum advance angle amount in this case is determined by the spindle (25) coming into contact with the elongated hole (15a). In addition, as mentioned above, the torque transmitted to the movable play (15) is determined by the rotational speed of the rotating shaft (3), but as with conventional devices, the angular acceleration of the rotating shaft (3) fluctuates rapidly. do. However, even if the angular acceleration of the drive member (18) fixed to the rotating shaft (3) fluctuates rapidly like the rotating shaft (3), the driven member (19) will not move due to its inertia.
To generate stable torque without following sudden angular acceleration fluctuations of the drive member (18).
また、第９図及び第１０図はこの考案の他の実施態様を
示すもので、（２８）は回転軸（３）に固着され、外周
にはファン（２８ａ）を有するドライブメンバ、（２９
）はこのドライブメンバ（２８）を間隙を介して包囲す
るよう配置されたドリグンメンバで、内周に設けられた
ベアリング（２９ａ）によって回転軸（３）に回動自在
に支承されている。（２９ａ）は上記ドライブメンバ（
２８）のファン（２８ａ）と対向するように、上記ドリ
グンメンバ（２９）の内周に設けられたファン、（３０
）Ｆｉ上上記ドラダグメンバ２８）と上記ドリグンメン
バ（２９）との間隙に、シールリング（３１）によって
密封された粘性を有する流体、例えば油である。Further, FIGS. 9 and 10 show another embodiment of this invention, in which (28) is a drive member fixed to the rotating shaft (3) and has a fan (28a) on the outer periphery;
) is a driven member disposed so as to surround the drive member (28) with a gap therebetween, and is rotatably supported on the rotating shaft (3) by a bearing (29a) provided on the inner periphery. (29a) is the drive member (
A fan (30) is provided on the inner periphery of the driven member (29) to face the fan (28a) of (28).
)Fi A viscous fluid, such as oil, is sealed by a seal ring (31) in the gap between the drag member 28) and the drag member (29).
なお、上記ドライブメンバ（２８）、上記ドリブンメン
バ（２９）、上記前（３０）、及び上記シールリング（
（９）
３１）ですべり連結手段を構成している。このように構
成されたものにおいては、回転軸（３）の回転、即ち、
ドライブメンバ（２８）の回転により、油（３０）が回
転し、ドリグンメンバ（２９）にトルクを発生させる。Note that the drive member (28), the driven member (29), the front (30), and the seal ring (
(9) 31) constitutes a sliding connection means. In the device configured in this way, the rotation of the rotating shaft (3), that is,
The rotation of the drive member (28) causes the oil (30) to rotate and generate torque in the driven member (29).
更に、上記説明ではカム（１１）は回転軸（３）に装着
されたもので説明したが、カム（１１）は回転軸（３）
と一体的に形成してもよく、このように構成するとＸ部
品点数が減少できる効果がある。Furthermore, in the above explanation, the cam (11) was attached to the rotating shaft (3), but the cam (11) was attached to the rotating shaft (3).
It may be formed integrally with the X component, and this configuration has the effect of reducing the number of parts.
この発明は以上のように、回転軸と点火時期決定部材と
をすべり連結手段を介して連結し、回転軸の回転速度に
応じて上記すべり連結手段に生じたトルクにより、上記
点火時期決定部材を回動させ、点火時期を制御するよう
にしたので、回転軸急
の當激な角加速度変化の影響及び進角機構の慣性作用の
影響を最小限に抑制でき、安定し九進角特性が得られる
とともに進角機構が回転振動の影響を受けに＜＜、耐久
性を向上できる効果がある。As described above, the present invention connects the rotating shaft and the ignition timing determining member via the sliding connecting means, and the ignition timing determining member is connected by the torque generated in the sliding connecting means according to the rotational speed of the rotating shaft. Since the ignition timing is controlled by rotating the ignition timing, it is possible to minimize the effects of sudden and drastic changes in the angular acceleration of the rotating shaft and the effects of the inertia of the advance mechanism, resulting in stable nine-advance characteristics. At the same time, the advance angle mechanism is not affected by rotational vibration and has the effect of improving durability.
第１図は従来装置を示す断面正面図、第２図は（１０）
従来装置の点火時期決定機構を示す平面図、第３示す平
面図である。第４図はこの考案の一実施例を示す断面正
面図、第５図はこの考案の一実施例の点火時期決定機構
を示す平面図、第６図はこの考案の一実施例を示す断面
平面図、第７図はこの考案の一実施例を示すドライブメ
ンバの外周展開図、第８図はこの考案の一実施例を示す
ドリグンメンバの側部内周展開図、第９図はこの考案の
他の実施例を示す部分断面正面図、第１０図はこの考案
の他の実施例を示す断面平面図である。
図において、（３）は回転軸、（１１）はカム、（１５
）は可動プレート、（１６）は断続器、（１８） Ｆｉ
ドライグメンパ、（１９）はドリグンメンバ、 （２１
）は外ギヤ、（２３）はギヤ、（２４）は内ギヤ、（２
５）はスピンドル、（２６）けばね掛け、（２７）はス
プリングである。
なお、図中向−符′８は同一または相当部分を示す。
（１１）
第１図
第２図
第３図
第４図
第７図
第８図
第９図
第１０図FIG. 1 is a sectional front view showing a conventional device, FIG. 2 is a plan view (10) showing the ignition timing determining mechanism of the conventional device, and the third plan view is a plan view showing the ignition timing determining mechanism of the conventional device. Fig. 4 is a cross-sectional front view showing an embodiment of this invention, Fig. 5 is a plan view showing an ignition timing determining mechanism of an embodiment of this invention, and Fig. 6 is a sectional plane showing an embodiment of this invention. 7 is a developed view of the outer periphery of a drive member showing an embodiment of this invention, FIG. 8 is a developed view of the inner lateral side of a drive member showing an embodiment of this invention, and FIG. 9 is a developed view of another part of this invention. FIG. 10 is a partially sectional front view showing an embodiment, and FIG. 10 is a sectional plan view showing another embodiment of this invention. In the figure, (3) is the rotating shaft, (11) is the cam, and (15) is the rotating shaft.
) is the movable plate, (16) is the interrupter, (18) Fi
Dorigumenpa, (19) is Dorigumenpa, (21
) is the outer gear, (23) is the gear, (24) is the inner gear, (2
5) is a spindle, (26) is a spring hook, and (27) is a spring. Note that the arrow '8' in the figure indicates the same or equivalent part. (11) Figure 1 Figure 2 Figure 3 Figure 4 Figure 7 Figure 8 Figure 9 Figure 10
Claims (3)
軸の回転に応じて点火時期を決定する点火時期決定部材
、この点火時期決定部材が装着され、上記回転軸の周り
に回動自在に設けられた可動プレート、上記回転軸に対
してすべり連結され、上記回転軸の回転速度に応じたト
ルクを発生するすべり連結手段、及び上記すべり連結手
段のトルクに応じて上記可動プレートを回動させる回動
手段を備えた機関点火時期制御装置。(1) A rotating shaft that rotates in synchronization with the rotation of the engine, an ignition timing determining member that determines the ignition timing according to the rotation of this rotating shaft, and this ignition timing determining member is attached and rotates around the rotating shaft. A movable plate freely provided, a sliding connection means that is slidingly connected to the rotating shaft and generates a torque according to the rotational speed of the rotating shaft, and the movable plate is rotated according to the torque of the sliding connecting means. An engine ignition timing control device equipped with a rotating means for moving the engine ignition timing.
を内設したドライブメンバと、このドライブメンバを包
囲するよう上記回転軸に回動自在に支承され、導体を内
設した磁性体より成るドリグンメンバとで構成されてい
ることを特徴とする特許請求の範囲第１項記載の機関点
火時期制御装置。(2) The sliding connection means includes a drive member that is fixed to the rotating shaft and has a permanent magnet inside, and a magnetic body that is rotatably supported on the rotating shaft so as to surround the drive member and has a conductor inside. The engine ignition timing control device according to claim 1, characterized in that the engine ignition timing control device is comprised of a driven member consisting of:
ァンを有するドライブメンバ吉、コノトライグメンパを
間隙を介して包囲するよう上記回転軸に回動自在に支承
され、上記ファンと対向する７アンを有したドリグンメ
ンバと、上記ドライブメンバと上記ドリグンメンバとの
間隙内に密封された粘性を有する流体とで構成されてい
ること全特徴とする機関点火時期制御装置。(3) The sliding connection means is fixed to the rotating shaft, is rotatably supported on the rotating shaft so as to surround the drive member KITSU, which has a fan on its outer periphery, through a gap, and is opposed to the fan. 1. An engine ignition timing control device comprising: a driven member having a 7 am angle; and a viscous fluid sealed in a gap between the drive member and the driven member.
Priority Applications (3)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12340182A JPS5912161A (en) | 1982-07-13 | 1982-07-13 | Controller for ignition timing of engine |
| DE19833325164 DE3325164A1 (en) | 1982-07-13 | 1983-07-12 | Ignition distributor |
| FR8311627A FR2530295B1 (en) | 1982-07-13 | 1983-07-12 | IGNITION DISTRIBUTOR |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12340182A JPS5912161A (en) | 1982-07-13 | 1982-07-13 | Controller for ignition timing of engine |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5912161A true JPS5912161A (en) | 1984-01-21 |
| JPS636742B2 JPS636742B2 (en) | 1988-02-12 |
Family
ID=14859638
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12340182A Granted JPS5912161A (en) | 1982-07-13 | 1982-07-13 | Controller for ignition timing of engine |
Country Status (3)
| Country | Link |
|---|---|
| JP (1) | JPS5912161A (en) |
| DE (1) | DE3325164A1 (en) |
| FR (1) | FR2530295B1 (en) |
Families Citing this family (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US4926013A (en) * | 1987-09-16 | 1990-05-15 | Mitsubishi Denki Kabushiki Kaisha | Distributor cap with molded cable terminals |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5234325U (en) * | 1975-09-01 | 1977-03-10 | ||
| JPS5280331U (en) * | 1975-12-13 | 1977-06-15 | ||
| JPS5741411U (en) * | 1980-08-15 | 1982-03-06 |
Family Cites Families (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| US3662726A (en) * | 1970-04-13 | 1972-05-16 | Gen Motors Corp | Distributor drive arrangement |
| US3882289A (en) * | 1972-02-28 | 1975-05-06 | Oak Industries Inc | Binary coded rotary wafer type switch assembly |
| DE2630220A1 (en) * | 1976-07-06 | 1978-01-19 | Bosch Gmbh Robert | DISTRIBUTOR FOR COMBUSTION MACHINERY |
| DE2636651C2 (en) * | 1976-08-14 | 1984-09-06 | Robert Bosch Gmbh, 7000 Stuttgart | Ignition distributors for internal combustion engines |
| JPS54113734A (en) * | 1978-02-24 | 1979-09-05 | Hitachi Ltd | Contactless type distributor |
| DE3041335A1 (en) * | 1980-11-03 | 1982-06-16 | Robert Bosch Gmbh, 7000 Stuttgart | Ignition distributor for internal combustion engines - has low profile internal section permitting smaller coil construction |
-
1982
- 1982-07-13 JP JP12340182A patent/JPS5912161A/en active Granted
-
1983
- 1983-07-12 FR FR8311627A patent/FR2530295B1/en not_active Expired
- 1983-07-12 DE DE19833325164 patent/DE3325164A1/en active Granted
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5234325U (en) * | 1975-09-01 | 1977-03-10 | ||
| JPS5280331U (en) * | 1975-12-13 | 1977-06-15 | ||
| JPS5741411U (en) * | 1980-08-15 | 1982-03-06 |
Also Published As
| Publication number | Publication date |
|---|---|
| FR2530295B1 (en) | 1987-10-16 |
| DE3325164C2 (en) | 1987-12-23 |
| JPS636742B2 (en) | 1988-02-12 |
| FR2530295A1 (en) | 1984-01-20 |
| DE3325164A1 (en) | 1984-05-03 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP4113811B2 (en) | Valve timing adjustment device | |
| JPS5912161A (en) | Controller for ignition timing of engine | |
| US2823655A (en) | Valve timing mechanism | |
| EP0648311B1 (en) | Phase change mechanism | |
| JP4388626B2 (en) | Active control valve for piston compressor and piston compressor provided with the valve | |
| US4941443A (en) | Governor device for an engine | |
| US4744339A (en) | Centrifugal spark-advance control device | |
| JPS63136987A (en) | Power generator using permanent magnet | |
| JPS5912162A (en) | Controller for ignition timing of engine | |
| US3080020A (en) | Centrifugal governor | |
| US2605753A (en) | Current generating device | |
| US2829507A (en) | Coupling | |
| US3198974A (en) | Ignition distributor | |
| US2982805A (en) | Ignition system for internal combustion engines | |
| JPH0861214A (en) | Permanent engine | |
| JPS5912163A (en) | Controller for ignition timing of engine | |
| JP2571705B2 (en) | Slow rotary solenoid | |
| ES8501482A1 (en) | Engine camshaft drive mechanism. | |
| JPS5830126Y2 (en) | Centrifugal advance device | |
| JPS60131066A (en) | Reciprocatingly drive device | |
| KR100507088B1 (en) | Continuously variable valve timing apparatus | |
| JPS61182463A (en) | Distributor for internal-combustion engine | |
| JP3448625B2 (en) | Flywheel for ignition device | |
| EP0356151B1 (en) | Centrifugal advance mechanism | |
| JPS6229637B2 (en) |