JPH01182651A - Variable inertial moment flywheel - Google Patents

Variable inertial moment flywheel

Info

Publication number
JPH01182651A
JPH01182651A JP63002249A JP224988A JPH01182651A JP H01182651 A JPH01182651 A JP H01182651A JP 63002249 A JP63002249 A JP 63002249A JP 224988 A JP224988 A JP 224988A JP H01182651 A JPH01182651 A JP H01182651A
Authority
JP
Japan
Prior art keywords
flywheel
main
sub
weight
force
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
Application number
JP63002249A
Other languages
Japanese (ja)
Inventor
Mitsutama Nakamura
中村　光瑶
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Nissan Motor Co Ltd
Original Assignee
Nissan Motor Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Nissan Motor Co Ltd filed Critical Nissan Motor Co Ltd
Priority to JP63002249A priority Critical patent/JPH01182651A/en
Publication of JPH01182651A publication Critical patent/JPH01182651A/en
Pending legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/1202—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon the damping action being at least partially controlled by centrifugal masses
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D43/18—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members with friction clutching members
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16F—SPRINGS; SHOCK-ABSORBERS; MEANS FOR DAMPING VIBRATION
    • F16F15/00—Suppression of vibrations in systems; Means or arrangements for avoiding or reducing out-of-balance forces, e.g. due to motion
    • F16F15/10—Suppression of vibrations in rotating systems by making use of members moving with the system
    • F16F15/12—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon
    • F16F15/1204—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system
    • F16F15/1205—Suppression of vibrations in rotating systems by making use of members moving with the system using elastic members or friction-damping members, e.g. between a rotating shaft and a gyratory mass mounted thereon with a kinematic mechanism or gear system with a kinematic mechanism, i.e. linkages, levers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16D—COUPLINGS FOR TRANSMITTING ROTATION; CLUTCHES; BRAKES
    • F16D43/00—Automatic clutches
    • F16D43/02—Automatic clutches actuated entirely mechanically
    • F16D43/04—Automatic clutches actuated entirely mechanically controlled by angular speed
    • F16D43/14—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members
    • F16D2043/145—Automatic clutches actuated entirely mechanically controlled by angular speed with centrifugal masses actuating the clutching members directly in a direction which has at least a radial component; with centrifugal masses themselves being the clutching members the centrifugal masses being pivoting

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Acoustics & Sound (AREA)
  • Aviation & Aerospace Engineering (AREA)
  • Mechanical Operated Clutches (AREA)

Abstract

PURPOSE:To prevent any engine stall at a time when engine speed is quickly lowered or the like and vibration from occurring by installing a main flywheel clamped to a driving shaft, a sub-flywheel supported as relatively rotatable to the former, and a weight, a contact part and a spring member in this sub- flywheel, respectively. CONSTITUTION:When a drop in engine speed is so quick, rotational speed of a main flywheel 2 becomes slower than that of a sub-flywheel 3, and a rocking weight 4 receives clockwise force to a shaft center at time of a friction plate 5. At this time, a position of a pin 6 and a position of the friction plate 5 are set so as to cause a perpendicular direction of a contact face at a contact point of the friction plate 5 and a direction of reaction force added with surface pressure and frictional force to hold this pin 6 in between. Consequently, counterclockwise force centering on the pin 6 is added to the weight 4, and pressing force against the main flywheel 2 by the friction plate 5 increases, whereby these main and sub flywheels 2, 3 are coupled together at once and solidly rotated. Moreover, the sub-flywheel 3 has already stored rotational energy, so that any drop in engine speed is thus prevented from occurring.

Description

【発明の詳細な説明】 （産業上の利用分野） 本発明は、自動車のクランク軸等に設ける可変慣性能率
フライホイールに関する。DETAILED DESCRIPTION OF THE INVENTION (Field of Industrial Application) The present invention relates to a variable inertia rate flywheel provided on a crankshaft of an automobile or the like.

（従来の技術） 従来の可変慣性能率フライホイールとしては、例えば、
特開昭６１−１０３０２６号公報に記載されたものが知
られている。(Prior art) Conventional variable inertia flywheels include, for example,
The one described in Japanese Unexamined Patent Publication No. 61-103026 is known.

この従来の可変慣性能率フライホイールは、高回転にな
ると増加する遠心力を利用して主フライホイールからイ
ナーシャディスク（副フライホイール）を切り離し、慣
性能率を減少させるものであった （発明が解決しようとする問題点） しかしながら、従来の可変慣性能率フライホイールでは
、切り離されたイナーシャディスクは停止するため、次
に回転が低下して再度結合する場合、急速に結合すると
ショックが発生するし、これを避けるためにゆっくり結
合すると、急ブレーキ等でエンジン回転数が急速に低下
したとき等、エンジン回転が下がりすぎてエンストした
り、大きな振動が発生してしまう問題があった。This conventional variable inertia rate flywheel uses centrifugal force that increases as the rotation speed increases to separate the inertia disk (auxiliary flywheel) from the main flywheel, reducing the inertia rate. However, in conventional variable inertia flywheels, the separated inertia disks stop, so when the rotation decreases and they are reconnected, rapid reconnection causes a shock. If the engine is connected slowly to avoid this, there is a problem that when the engine speed drops rapidly due to sudden braking, etc., the engine speed drops too much, causing the engine to stall or causing large vibrations.

（問題点を解決するための手段） 本発明は上述のような従来の問題点を解決するためにな
されたもので、そのために本発明では、駆動軸に固定さ
れた主フライホイールと、該主フライホイールに対して
相対回転可能に支持された副フライホイールと、副フラ
イホイールに、ホイール回転方向の動きを規制されなが
ら、重心位置が半径方向に移動可能に支持された重錘と
、該重錘の重心の半径方向位置が増加した時に、主フラ
イホイール又は主フライホイールと共に回転する部材へ
の押圧力が減少するように連動する接触部と、重錘を重
心の半径方向位置が減少する方向に付勢するばね部材と
を備えた可変慣性能率フライホイールを構成した。(Means for Solving the Problems) The present invention has been made to solve the above-mentioned conventional problems, and for this purpose, in the present invention, a main flywheel fixed to a drive shaft and a main flywheel fixed to a drive shaft, A sub-flywheel supported to be rotatable relative to the flywheel; a weight supported by the sub-flywheel such that its center of gravity can be moved in a radial direction while movement in the wheel rotational direction is regulated; A contact part that operates in such a way that the pressing force on the main flywheel or a member rotating together with the main flywheel decreases when the radial position of the center of gravity of the weight increases, and a contact part that moves the weight in a direction in which the radial position of the center of gravity decreases. A variable inertia rate flywheel was constructed, which included a spring member that biased the flywheel.

（作　用） エンジンの回転が低回転の時は、ばね部材により重錘は
重心の半径方向位置が減少する方向に付勢されているの
で、接触部が主フライホイールに押し付けられ、その摩
擦力によって副フライホイールは重錘を介して主フライ
ホイールと一体に回転し、このときの慣性モーメントは
大である。(Function) When the engine is rotating at low speeds, the spring member biases the weight in a direction that reduces the radial position of the center of gravity, so the contact part is pressed against the main flywheel, and the friction force The secondary flywheel rotates together with the main flywheel via the weight, and the moment of inertia at this time is large.

次に、エンジンの回転が低回転から上昇して重錘にかか
る遠心力が増加すると、重錘はばね部材に抗して重心の
半径方向位置を増加する方向に移動しようとするので、
接触部の主フライホイールに対する押圧力が低下し、こ
れが所定回転数以上になると、接触部が主フライホイー
ルから離れ主フライホイールから副フライホイールが分
離する。しかし、副フライホイールが分離すると、その
回転が下がり、重錘にかかかる遠心力が低下するので、
ばね部材により接触部が主フライホイールに押し付けら
れて、副フライホイールは再度主フライホイールと一体
に回転することになり、結局、接触部は主フライホイー
ルに対して滑りながら軽く接触した状態を維持し、副フ
ライホイールは停止することなく回転し続ける。Next, when the rotation of the engine increases from low rotation and the centrifugal force applied to the weight increases, the weight tries to move in a direction that increases the radial position of the center of gravity against the spring member.
When the pressing force of the contact portion against the main flywheel decreases and reaches a predetermined number of revolutions or more, the contact portion separates from the main flywheel and the sub flywheel separates from the main flywheel. However, when the secondary flywheel separates, its rotation decreases and the centrifugal force applied to the weight decreases.
The contact part is pressed against the main flywheel by the spring member, and the sub flywheel rotates together with the main flywheel again, and in the end, the contact part remains in light contact with the main flywheel while sliding. However, the secondary flywheel continues to rotate without stopping.

又、エンジンの回転が所定回転数以下に低下する場合、
その回転低下が徐々であれば、副フライホイールも主フ
ライホイールとほぼ同様に回転低下し、重錘にかかる遠
心力がばね部材の付勢力よりも小さくなるので、接触部
が主フライホイールに押し付けられ、副フライホイール
は主フライホイールと一体に回転し、慣性モーンメント
は大である。Also, if the engine rotation drops below the specified rotation speed,
If the rotation decreases gradually, the rotation of the sub-flywheel will decrease in almost the same way as the main flywheel, and the centrifugal force applied to the weight will be smaller than the biasing force of the spring member, so the contact part will press against the main flywheel. The auxiliary flywheel rotates together with the main flywheel, and the moment of inertia is large.

そして、エンジンの回転低下が急速の場合には、副フラ
イホイールよりも主フライホイールの回転速度が遅くな
るので、接触部の主フライホイールとの接触点には、重
錘の重心の半径方向位置を減少させる方向に力が働き、
これにばね部材による付勢力が加わるために接触部が主
フライホイールに押し付けられ、副フライホイールは直
ちに主フライホイールと一体に回転し、かつ、この副フ
ライホイールには回転維持によって既に回転エネルギー
が蓄えられているので、主フライホイールとの結合時に
ショックが発生するこ′とがないし、エンジン回転の低
下に伴なうエンストや振動の発生を招くことはない。If the engine speed decreases rapidly, the rotational speed of the main flywheel will be slower than that of the sub-flywheel, so the radial position of the center of gravity of the weight will be at the point of contact with the main flywheel. A force acts in the direction of decreasing
Since the biasing force of the spring member is added to this, the contact portion is pressed against the main flywheel, and the sub flywheel immediately rotates together with the main flywheel, and the sub flywheel already has rotational energy due to the maintenance of rotation. Since it is stored, there is no shock when it is connected to the main flywheel, and there is no possibility of engine stalling or vibration caused by a drop in engine speed.

（実施例） 以下、本発明の実施例を図面により詳述する。(Example) Hereinafter, embodiments of the present invention will be described in detail with reference to the drawings.

尚、以下に述べる各実施例において、同一構成部分につ
いては図面上の符合を同一にして、その説明を省略する
。In each of the embodiments described below, the same constituent parts are given the same reference numerals in the drawings, and their explanation will be omitted.

第１図及び第２図は第１実施例の可変慣性能率フライホ
イールＡを示している。1 and 2 show a variable inertia rate flywheel A according to a first embodiment.

■は駆動軸としてのエンジンのクランクシャフト、２は
主フライホイールで、前記クランクシャフトｌの端部に
固定されている。３は副フライホイールで、主フライホ
イール２にベアリング３ａを介して回動可能に装着され
ている。2 is the engine crankshaft as a drive shaft; 2 is the main flywheel, which is fixed to the end of the crankshaft 1; A sub-flywheel 3 is rotatably mounted on the main flywheel 2 via a bearing 3a.

４は揺動重錘で、副フライホイール３にビン６によって
揺動可能に支持されることで、フライホイールの回転方
向（矢印Ｍ方向）の動きを規制されながら、重心５０の
位置が半径方向に移動可能になっている。Reference numeral 4 denotes a swinging weight, which is swingably supported by the sub-flywheel 3 by the bin 6, so that the position of the center of gravity 50 is adjusted in the radial direction while the movement in the rotational direction of the flywheel (in the direction of arrow M) is restricted. It is possible to move to.

５は接触部としての摩擦板で、揺動重錘４の外周面に貼
付され、揺動重錘４が反時計方向（重心５０の半径方向
位置が減少する方向）に回動することで、主フライホイ
ール２に押し付けられ、時計方向（重心５０の半径方向
位置が増加する方向）に回動することで、主フライホイ
ール２から離反する。Reference numeral 5 denotes a friction plate as a contact part, which is attached to the outer peripheral surface of the swinging weight 4, and when the swinging weight 4 rotates in a counterclockwise direction (direction in which the radial position of the center of gravity 50 decreases), It is pressed against the main flywheel 2 and rotates clockwise (in the direction in which the radial position of the center of gravity 50 increases), thereby separating from the main flywheel 2.

７はばね部材で、副フライホイール３に固定されたピン
８と揺動重錘４に固定されたピン９との間に装着され、
揺動重錘５を反時計方向に付勢している。7 is a spring member, which is installed between a pin 8 fixed to the sub flywheel 3 and a pin 9 fixed to the swinging weight 4;
The swinging weight 5 is urged counterclockwise.

次に、第１実施例の作用を説明する。Next, the operation of the first embodiment will be explained.

エンジン駆動によるクランクシャフト１の回転によって
王フライホイール２が回転し、その回転が低回転の時は
、ばね部材７により揺動重錘４が反時計方向に付勢され
ているので、摩擦板５は主フライホイール２に押圧され
、その摩擦力によって副フライホイール３は揺動重錘４
を介して主フライホイール２と結合し一体に回転する。The rotation of the crankshaft 1 driven by the engine rotates the king flywheel 2, and when the rotation is low, the swinging weight 4 is biased counterclockwise by the spring member 7, so the friction plate 5 is pressed by the main flywheel 2, and the auxiliary flywheel 3 is pushed by the oscillating weight 4 due to the frictional force.
It is connected to the main flywheel 2 via the main flywheel 2 and rotates together.

このときの慣性モーメントは大きく、エンジン回転は安
定する。At this time, the moment of inertia is large, and the engine rotation becomes stable.

エンジンが低回転域から上昇すると、接触重錘４にかか
る遠心力が増加し、該揺動重錘４はばね部材７に抗して
時計方向に回動しようとするので、摩擦板５による主フ
ライホイール１への押圧力が低下し、これが所定回転数
以上になると、主フライホイール２から離れ、副フライ
ホイール３は主フライホイール２から分離する。When the engine rises from the low speed range, the centrifugal force applied to the contact weight 4 increases, and the swinging weight 4 tries to rotate clockwise against the spring member 7. When the pressing force on the flywheel 1 decreases and reaches a predetermined number of revolutions or more, it separates from the main flywheel 2 and the sub flywheel 3 separates from the main flywheel 2.

しかし、副フライホイール３が分離すると、その回転が
下がって揺動重錘４にかかる遠心力も低下するので、ば
ね部材７により摩擦板５が主フライホイール２に押圧さ
れ、主、副フライホイール２．３が結合するので、結局
は摩擦板５が主フライホイール２に対して滑りながら軽
く接触した状態を維持し、副フライホイール３は分離状
態で回転し続ける。このとき慣性モーメントは小さく、
エンジンの加速応答性が向上する。However, when the sub flywheel 3 separates, its rotation decreases and the centrifugal force applied to the oscillating weight 4 also decreases, so the friction plate 5 is pressed against the main flywheel 2 by the spring member 7, causing the main and sub flywheels to .3 are connected, so that the friction plate 5 ultimately maintains a state in which it is in slight contact with the main flywheel 2 while sliding, and the sub-flywheel 3 continues to rotate in a separated state. At this time, the moment of inertia is small,
Improves engine acceleration response.

エンジンの回転が高回転域から低下する場合、その回転
低下が徐々であれば、副フライホイール３は主フライホ
イール２とほぼ同様に回転低下するので、揺動重錘４に
かかる遠心力よりもばね部材７の付勢力よりも小さくな
った時点で、主、副フライホイール２．３が結合し一体
に回転する。When the rotation of the engine decreases from a high rotation range, if the rotation decreases gradually, the rotation of the sub flywheel 3 decreases in almost the same way as the main flywheel 2, so that the centrifugal force exerted on the swinging weight 4 is When the biasing force becomes smaller than the biasing force of the spring member 7, the main and sub flywheels 2.3 are connected and rotate together.

そして、エンジンの回転低下が急速の場合には、副フラ
イホイール３よりも主フライホイール２の回転速度が遅
くなり、揺動重錘４は摩擦板５の時点で軸心に対して反
時計方向の力を受ける。When the engine speed decreases rapidly, the rotational speed of the main flywheel 2 becomes slower than that of the sub-flywheel 3, and the oscillating weight 4 moves counterclockwise with respect to the axis at the time of the friction plate 5. receive the power of

この時、摩擦板５の接触点での接触面の垂線方向と、面
圧と摩擦力を加えた反力の方向がピン６を挟むように、
ピン６の位置と摩擦板５の位置が設定されているので、
揺動重錘４にはピン６を中心とした反時計方向の力が加
わり、摩擦板５による王フライホイール２に対する押圧
力が増加し、主、副フライホイール２．３は直ちに結合
して一体に回転し、しかも副フライホイール３は既に回
転エネルギーを蓄えているので、エンジンの回転低下を
防ぐことができるし、結合時のショック発生を防止でき
る。At this time, the perpendicular direction of the contact surface at the contact point of the friction plate 5 and the direction of the reaction force, which is the addition of surface pressure and friction force, sandwich the pin 6.
Since the position of pin 6 and the position of friction plate 5 are set,
A counterclockwise force centered on the pin 6 is applied to the oscillating weight 4, and the pressing force against the king flywheel 2 by the friction plate 5 increases, and the main and sub flywheels 2.3 are immediately connected and integrated. Moreover, since the sub flywheel 3 has already stored rotational energy, it is possible to prevent a decrease in engine rotation and also to prevent the occurrence of shock when the engine is coupled.

尚、上記の実施例では、重錘をピン６により副フライホ
イール３に揺動可能に支持した揺動重錘４としたが、重
錘の副フライホイールに対する動きは、回転方向には規
制されながら、重心の半径方向位置が変化するものであ
れば、例えば、案内面に沿っての摺動や転勤であっても
よく、その半径方向位置を減する移動によって、接触部
の主フライホイールに対する押圧力が増加するように構
成されていればよい。In the above embodiment, the weight is the oscillating weight 4 which is swingably supported on the sub-flywheel 3 by the pin 6, but the movement of the weight with respect to the sub-flywheel is not restricted in the rotational direction. However, as long as the radial position of the center of gravity changes, it may be, for example, sliding or shifting along a guide surface, and the movement that reduces the radial position of the contact part relative to the main flywheel It is sufficient if the configuration is such that the pressing force increases.

又、主フライホイールが副フライホイールよりも回転速
度が遅くなった場合、接触部で主フライホイールから受
ける力によって接触圧力が増加するように構成されてい
ることが望ましい、即ち、このとき副フライホイールが
主フライホイールから受ける力は、副フライホイールの
回転を止める方向であるので、この場合に重錘が受ける
力が、上記実施例のように、摩擦板を主フライホイール
に押圧させる方向の回転力を生ずるもの以外に、揺動し
た際の動きが接触圧を高める方向のくさびとか、揺動叉
は摺動、転動がテコの作用によって接触圧を高める機構
であってもよい。In addition, when the rotational speed of the main flywheel becomes slower than that of the sub flywheel, it is desirable that the contact pressure is increased by the force received from the main flywheel at the contact portion. The force that the wheel receives from the main flywheel is in the direction of stopping the rotation of the sub flywheel, so the force that the weight receives in this case is in the direction of pressing the friction plate against the main flywheel, as in the above example. In addition to the mechanism that generates rotational force, it may be a wedge in which the movement when rocking increases the contact pressure, or a mechanism that increases the contact pressure by the action of rocking, sliding, or rolling as a lever.

次に、第３図及び第４図は第２実施例の可変慣性能率フ
ライホイールＢを示している。Next, FIGS. 3 and 4 show a variable inertia ratio flywheel B according to a second embodiment.

１６は揺動重錘支持用のピンで、第１実施例の場合より
も外方に設けられている。Reference numeral 16 denotes a pin for supporting the swinging weight, which is provided further outward than in the first embodiment.

１９はばね部材用のピンで、第１実施例の場合と取り付
は位置、取り付は向きが異なる。Reference numeral 19 denotes a pin for a spring member, and the mounting position and mounting direction are different from those in the first embodiment.

２０はシューで、Ｔ字型断面形状に形成されて、揺動重
錘４の外周に形成された溝４ａ内に嵌め込まれ、かつ該
シュー２０の外周面には全面に亘って摩擦板１５が貼付
されている。Reference numeral 20 denotes a shoe, which is formed into a T-shaped cross section and is fitted into a groove 4a formed on the outer periphery of the swinging weight 4, and a friction plate 15 is provided over the entire outer periphery of the shoe 20. It is affixed.

２２．２３は（さび型ピースで、円柱部材の一端が斜め
にカットされ、両くさび型ピース２２，２３はカット面
同士が血合され、かつ一方のくさび型ピース２２は揺動
重錘４内に摺動可能に嵌合され、その内部に嵌装したス
プリング２４により押しネジ２１に押し付けられ、又、
他方のくさび型ピース２３は、端面で前記シュー２０の
下端を支える状態で上下方向に摺動可能に嵌合され、そ
して、一方のくさび型ピース２２を押しネジ２１の進退
により移動することで他方のくさび型ピース２３を上下
摺動させて、シュー２０の支持位置を上下調整する構造
となっている。22 and 23 are (wedge-shaped pieces, one end of a cylindrical member is cut diagonally, the cut surfaces of both wedge-shaped pieces 22 and 23 are joined together, and one wedge-shaped piece 22 is placed in the swinging weight 4. It is slidably fitted and pressed against the set screw 21 by a spring 24 fitted therein, and
The other wedge-shaped piece 23 supports the lower end of the shoe 20 with its end face and is fitted so as to be slidable in the vertical direction, and by moving one wedge-shaped piece 22 by moving the push screw 21 back and forth, the other wedge-shaped piece 23 can be moved. The support position of the shoe 20 can be adjusted up and down by sliding the wedge-shaped piece 23 up and down.

又、２５はブロックで、副フライホイール３に斜め向き
に固定され、シュー２０の端部に形成した切欠き部２６
内に嵌合され、内部に嵌装したスプリング２５ｂにより
シュー２０を摩擦板１５が主フライホイール２から離反
する方向に付勢している。Further, 25 is a block, which is diagonally fixed to the sub flywheel 3, and has a notch 26 formed at the end of the shoe 20.
The shoe 20 is biased in the direction in which the friction plate 15 moves away from the main flywheel 2 by a spring 25b fitted inside.

２７は戻しスプリングで、シュー２０を摩擦板１５が王
フライホイール２から離反する方向に付勢している。A return spring 27 biases the shoe 20 in a direction in which the friction plate 15 moves away from the king flywheel 2.

従って、この第２実施例では、摩擦板１５の主フライホ
イール２に対する接触面が大きく耐久性が向上すると共
に、摩擦ｍ１５と主フライホイール２との間隙調整が可
能となる。Therefore, in this second embodiment, the contact surface of the friction plate 15 with the main flywheel 2 is large and durability is improved, and the gap between the friction m15 and the main flywheel 2 can be adjusted.

そして、低回転時の押圧力は、ばね部材７による揺動重
錘４の反時計方向の回動でくさび型ピース２３によりシ
ュー２０を押圧することによって得られる。The pressing force during low rotation is obtained by pressing the shoe 20 with the wedge-shaped piece 23 by counterclockwise rotation of the swinging weight 4 by the spring member 7.

又、主フライホイール２が副フライホイール３よりも回
転が遅くなった場合は、摩擦板１５の接触面が主フライ
ホイール２から受ける力は、フライホイールの回転方向
と逆の方向になる為、シュー２０は切欠き部２６でブロ
ック２５の傾斜面２５ａにガイドされながら外方に摺動
し、摩擦板１５が主フライホイール２に押圧されて接触
圧力が増加する。これに伴ない副フライホイール３の回
転は低下して遠心力が減少し、この点からも接触圧力が
増加するので、副フライホイール３が主フライホイール
２から受ける力は更に増加し、主、副フライホイール２
．３は急速に結合し、副フライホイール３が蓄えていた
回転エネルギーによってエンジン回転が急速に低下する
のを防ぐことができる６ 尚、本実施例でピン１６を外方に設けたのは、揺動重錘
４の重心５０には、半径方向外方（イ方向）に遠心力が
働くほか、回転速度が変動したときの慣性力がこれと直
角の方向（口方向）に作用し、この力がピン１６に対し
てモーメントを持つと、それによって揺動重錘４からシ
ュー２０に作用する押圧力が変化するので、それを避け
るため慣性力の方向（口方向）と−直線になるようにピ
ン１６の中心を設定するようにした。Also, if the main flywheel 2 rotates slower than the sub flywheel 3, the force that the contact surface of the friction plate 15 receives from the main flywheel 2 will be in the opposite direction to the rotational direction of the flywheel. The shoe 20 slides outward while being guided by the inclined surface 25a of the block 25 at the notch 26, and the friction plate 15 is pressed against the main flywheel 2, increasing the contact pressure. Along with this, the rotation of the sub flywheel 3 decreases and the centrifugal force decreases, and the contact pressure increases from this point as well, so the force that the sub flywheel 3 receives from the main flywheel 2 further increases, and the main Sub flywheel 2
．． 3 are quickly connected, and the rotational energy stored in the sub flywheel 3 can prevent the engine rotation from rapidly decreasing. Centrifugal force acts on the center of gravity 50 of the dynamic weight 4 outward in the radial direction (direction A), and inertial force when the rotational speed fluctuates acts in a direction perpendicular to this (in the mouth direction). If it has a moment with respect to the pin 16, the pressing force acting on the shoe 20 from the swinging weight 4 will change, so in order to avoid this, the The center of pin 16 is now set.

又、ピン１６の位置を更に外方に設定することで、慣性
力により回転低下時の押圧力を増加させて主フライホイ
ール２の回転低下時の結合をより早める効果を持たせた
り、ピン１６をより内方に設定することにより、エンジ
ンの爆発によるトルクビーク時に主フライホイール２の
回転速度が一瞬速くなることによる副フライホイール３
との間のスリップ発生を避けるようにすることも可能で
ある。In addition, by setting the pin 16 further outward, the inertia force increases the pressing force when the rotation decreases, which has the effect of accelerating the connection when the rotation of the main flywheel 2 decreases. By setting more inward, the rotational speed of the main flywheel 2 momentarily increases during torque peak due to engine explosion, which causes the rotational speed of the sub flywheel 3 to increase.
It is also possible to avoid slippage between the two.

次に、第５図は第３実施例の可変慣性能率フライホイー
ルＣを示している。Next, FIG. 5 shows a variable inertia rate flywheel C according to a third embodiment.

この実施例は、前記第２実施例では６個全てのシュー２
０にそれぞれブロック２５及び切欠き部２６が設けられ
ているのに対し、本実施例では、６個の揺動重錘４に対
して１つ置きのシュー３０の端部に突出部３１が形成さ
れ、この突出部３Ｉを隣りのシュー２０に接触させるよ
うに構成されている。In this embodiment, all six shoes 2 in the second embodiment are
0 are provided with blocks 25 and notches 26, respectively, whereas in this embodiment, protrusions 31 are formed at the ends of every other shoe 30 for the six swinging masses 4. The protruding portion 3I is configured to come into contact with the adjacent shoe 20.

この突出部３１をシュー２０に接触させることにより、
主フライホイール２が副フライホイール３よりも回転低
下した場合、シュー２０が主フライホイール２より受け
る力がそのままシュー３０に伝えられ、シュー３０の摩
擦板３２の接触圧力を増す方向に作用する。By bringing this protrusion 31 into contact with the shoe 20,
When the rotation of the main flywheel 2 is lower than that of the sub flywheel 3, the force that the shoe 20 receives from the main flywheel 2 is directly transmitted to the shoe 30, and acts in the direction of increasing the contact pressure of the friction plate 32 of the shoe 30.

従って、シュー３０は、該シュー３０自身が主フライホ
イール２から受ける力と、シュー２０から受ける力の両
方で非常に強い力で主フライホイール２に摩擦板３２を
押圧することとなり、主フライホイール２の回転が低下
したときの主、副フライホイール２．３の結合が急速に
なる。Therefore, the shoe 30 presses the friction plate 32 against the main flywheel 2 with a very strong force due to both the force that the shoe 30 itself receives from the main flywheel 2 and the force that it receives from the shoe 20. When the rotation of flywheel 2 decreases, the connection between the main and sub flywheels 2.3 becomes rapid.

第６図及び第７図は第４実施例の可変慣性能率フライホ
イールＤを示し、特に、主フライホイール２の回転が副
フライホイール３の回転よりも遅くなったときに、接触
部の接触圧力を増加して、主、副フライホイール２．３
が結合するまでの応答性の向上を図ることを目的として
いる。6 and 7 show a variable inertia flywheel D according to a fourth embodiment, and in particular, when the rotation of the main flywheel 2 becomes slower than the rotation of the sub flywheel 3, the contact pressure of the contact portion Increase the main and sub flywheels 2.3
The aim is to improve responsiveness until the two are combined.

４０はリンクで、副フライホイール３に設けたビン８と
シュー２０に設けたビン４１との間に設けられると共に
、シュー２０を主フライホイール２から引き離すように
作用するばね４２が設けられている。A link 40 is provided between the pin 8 provided on the sub flywheel 3 and the pin 41 provided on the shoe 20, and is provided with a spring 42 that acts to separate the shoe 20 from the main flywheel 2. .

そして、このリンク４０は、シュー２０の摩擦板１５に
主フライホイール２から回転方向と逆向きの力がかかっ
たとき、シュー２０を主フライホイール２に押圧する機
能を果すもので、前記第２実施例のブロック２５と同様
の作用を行ない、この場合、ブロック２５よりもリンク
４０の方が多くのスペースを必要とするが、摩擦が少な
いので作動が敏速になるという利点がある。The link 40 functions to press the shoe 20 against the main flywheel 2 when a force in the direction opposite to the rotating direction of the main flywheel 2 is applied to the friction plate 15 of the shoe 20. The link 40 performs the same function as the block 25 of the embodiment, and in this case, the link 40 requires more space than the block 25, but has the advantage of faster operation due to less friction.

４３は補助シューで、外周に摩擦板４４が貼付けられ、
かつ該補助シュー４３にビン連結されたリンク４５と、
前記シュー２０にビン連結されたリンク４６と、副フラ
イホイール３にビン連結されたリンク４７とがビン４８
によって同時に連結され、かつ補助シュー４３を摩擦板
４４が主フライホイール２に押圧する方向に付勢すると
共に、シュー２０を摩擦板１５が主フライホイール２か
ら離反する方向に付勢するねじつばね４９が設けられて
いる。43 is an auxiliary shoe, on the outer periphery of which a friction plate 44 is attached;
and a link 45 connected to the auxiliary shoe 43 via a bottle;
A link 46 connected to the shoe 20 and a link 47 connected to the sub flywheel 3 are connected to a pin 48.
screwed collars that are simultaneously connected by and bias the auxiliary shoe 43 in the direction in which the friction plate 44 presses against the main flywheel 2 and bias the shoe 20 in the direction in which the friction plate 15 moves away from the main flywheel 2; 49 are provided.

従って、補助シュー４３の摩擦板４４は常に主フライホ
イール２に軽く接触し、主フライホイール２が副フライ
ホイール３よりも早く回転している時は、主フライホイ
ール２より回転方向の力を受け、リンク４６を介してシ
ュー２０を主フライホイール２から引き離す方向に力を
与えると共に、リンク４７を介して副フライホイール３
に回転方向の力を伝えるもので、この場合、副フライホ
イール３への力は、摩擦板４４への接触圧が小さ（設定
されているので、副フライホイール３の所定回転数以上
に回転させるほど強くはない。Therefore, the friction plate 44 of the auxiliary shoe 43 always lightly contacts the main flywheel 2, and when the main flywheel 2 is rotating faster than the auxiliary flywheel 3, it receives a force from the main flywheel 2 in the rotational direction. , applies force in the direction of separating the shoe 20 from the main flywheel 2 via the link 46, and applies force to the sub flywheel 3 via the link 47.
In this case, the force to the sub-flywheel 3 is determined by the contact pressure to the friction plate 44 being small (as it is set, the sub-flywheel 3 is rotated at a predetermined rotational speed or higher). Not as strong as that.

又、主フライホイール２の回転が副フライホイール３の
回転より遅くなった時には、補助シュー４３に回転方向
と逆向きの力がかかり、３ケのリンク４５．４６．４７
を介してシュー２０に摩擦ｉ１５を主フライホイール２
に押圧する方向の力を与え、この場合、リンク角度の関
係から強い力で押圧すると共に、その反力で補助シュー
４３の摩擦板４４の接触圧力も高くなり、この作用によ
って応答性よくシュー２０の摩擦板１５の接触圧力を高
めることができる。Also, when the rotation of the main flywheel 2 becomes slower than the rotation of the sub flywheel 3, a force is applied to the auxiliary shoe 43 in the opposite direction to the rotation direction, and the three links 45, 46, 47
The friction i15 is applied to the shoe 20 through the main flywheel 2
In this case, due to the link angle, a strong force is applied to the auxiliary shoe 43, and the reaction force also increases the contact pressure of the friction plate 44 of the auxiliary shoe 43. This action causes the shoe 20 to respond with good response. The contact pressure of the friction plate 15 can be increased.

以上、本発明の詳細な説明してきたが、要するに本発明
は、所定回転数以下で、主、副フライホイールが結合し
、所定回転数以下で切離される遠心クラッチ機能と、遠
心クラッチが副フライホイール側に設けられ、主フライ
ホイールが所定回転数以上のときも副フライホイールは
停止することなく所定回転数で回転を維持する機能と、
主フライホイールの回転数が副フライホイールの回転数
より遅くなったとき、主、副フライホイールが直ちに結
合するワンウェイクラッチ機能の３つの機能を持つこと
を特徴とし、従って、従来一般のワンウェイクラッチに
利用されている多くの機構を応用できる。The present invention has been described in detail above, but in short, the present invention has a centrifugal clutch function in which the main and auxiliary flywheels are connected at a predetermined number of rotations or less and are disengaged at a predetermined number of rotations or less, and a centrifugal clutch is provided with a auxiliary flywheel. A function provided on the wheel side that allows the sub flywheel to maintain rotation at a predetermined rotation speed without stopping even when the main flywheel exceeds a predetermined rotation speed;
It is characterized by having three functions: a one-way clutch function that immediately engages the main and sub flywheels when the rotation speed of the main flywheel becomes slower than the rotation speed of the sub flywheel. Many of the mechanisms used can be applied.

（発明の効果） 以上説明してきたように、本発明の可変慣性能率フライ
ホイールにあっては、駆動軸に固定された主フライホイ
ールと、該王フライホイールに対して相対回転可能に支
持された副フライホイールと、副フライホイールに、ホ
イール回転方向の動きを規制されながら、重心位置が半
径方向に移動可能に支持された重錘と、該重錘の重心の
半径方向位置が増加した時に、主フライホイール又は主
フライホイールと共に回転する部材への押圧力が減少す
るように連動する接触部と１重錘を重心の半径方向位置
が減少する方向に付勢するばね部材と、を備えているこ
とを特徴とする構成とした為、以下に列挙する効果を同
時に達成することが出来る。(Effects of the Invention) As explained above, in the variable inertia flywheel of the present invention, the main flywheel fixed to the drive shaft and the king flywheel are supported so as to be rotatable relative to the main flywheel. A secondary flywheel, a weight supported by the secondary flywheel such that its center of gravity can move in the radial direction while its movement in the wheel rotational direction is restricted, and when the radial position of the center of gravity of the weight increases, It includes a contact portion that interlocks to reduce the pressing force on the main flywheel or a member that rotates together with the main flywheel, and a spring member that biases the single weight in a direction that reduces the radial position of the center of gravity. Since the structure is characterized by this, it is possible to simultaneously achieve the effects listed below.

■　エンジンが低速で回転している時は、主、副フライ
ホイールが結合し、大きな慣性モーメントでエンジンの
回転を安定させることができる。■ When the engine is rotating at low speed, the main and auxiliary flywheels are connected, creating a large moment of inertia that stabilizes the engine's rotation.

■　エンジンが高速している時は、副フライホイールが
主フライホイールから分離して慣性モーメントが小さく
なり、エンジンの加速応答性な向上させることができる
。■ When the engine is running at high speed, the auxiliary flywheel separates from the main flywheel, reducing the moment of inertia and improving the engine's acceleration response.

■　副フライホイールは主フライホイールから分離した
状態でも回転を維持し、かつ急ブレーキ等で王フライホ
イールの回転が副フライホイールの回転よりも遅くなっ
た場合に、主、副フライホイールが直ちに結合するので
、主フライホイールとの結合時にショックが発生するこ
とはない。■ The secondary flywheel maintains rotation even when separated from the main flywheel, and if the rotation of the main flywheel becomes slower than the rotation of the secondary flywheel due to sudden braking, etc., the main and secondary flywheels are immediately connected. Therefore, no shock occurs when connecting with the main flywheel.

■　エンジン回転の低下に伴なうエンストや振動を防止
して、エンジンの回転を安定させることができる。■ It is possible to stabilize engine rotation by preventing engine stalling and vibration caused by a drop in engine rotation.

【図面の簡単な説明】[Brief explanation of the drawing]

第１図は本発明第１実施例の可変慣性能率フライホイー
ルの正面図、第２図は第１図１−４断面図、第３図は本
発明第２実施例の可変慣性能率フライホイールの正面図
、第４図は第３図ＩＩ　−ＴＩ断面図、第５図は本発明
第３実施例の可変慣性能率フライホイールの正面図、第
６図は本発明第４実施例の可変慣性能率フライホイール
の正面図、第７図は第６図ｆｆｌ　−ＩＩＩ断面図であ
る。 Ａ・・−可変慣性能率フライホイール ■・・−クランク軸 ２・・・主フライホイール ３・・−副フライホイール ４・・−揺動重錘（重錘） ５・・−摩擦板 ７・・・バネ部材 ５０・−・重心Fig. 1 is a front view of a variable inertia ratio flywheel according to a first embodiment of the present invention, Fig. 2 is a sectional view taken from Fig. 1-4, and Fig. 3 is a front view of a variable inertia ratio flywheel according to a second embodiment of the present invention. A front view, FIG. 4 is a sectional view taken along line II-TI in FIG. 3, FIG. 5 is a front view of a variable inertia flywheel according to a third embodiment of the present invention, and FIG. 6 is a variable inertia ratio according to a fourth embodiment of the present invention. A front view of the flywheel, and FIG. 7 is a sectional view taken along line ffl-III in FIG. A... - Variable inertia rate flywheel ■... - Crankshaft 2... Main flywheel 3... - Sub flywheel 4... - Oscillating weight (weight) 5... - Friction plate 7...・Spring member 50 -- Center of gravity

Claims (1)

【特許請求の範囲】 １）駆動軸に固定された主フライホイールと、該主フラ
イホイールに対して相対回転可能に支持された副フライ
ホイールと、 副フライホイールに、ホイール回転方向の動きを規制さ
れながら、重心位置が半径方向に移動可能に支持された
重錘と、 該重錘の重心の半径方向位置が増加した時に、主フライ
ホイール又は主フライホイールと共に回転する部材への
押圧力が減少するように連動する接触部と、 重錘を重心の半径方向位置が減少する方向に付勢するば
ね部材と、 を備えていることを特徴とする可変慣性能率フライホイ
ール。 ２）主フライホイール又は主フライホイールと共に回転
する部材に設けられた円筒又は円錐状内面部に、副フラ
イホイール又は副フライホイールと共に回転する重錘と
連動関係にある接触部が接触することにより主フライホ
イールと副フライホイールとが互いに回転力を伝達し合
う様になっていて、重錘から接触部に及ぼす作用点と重
錘の重心との回転方向中間位置に、重錘の揺動支点があ
る事を特徴とする特許請求の範囲第１項記載の可変慣性
能率フライホイール。[Scope of Claims] 1) A main flywheel fixed to a drive shaft, a sub-flywheel supported so as to be rotatable relative to the main flywheel, and movement of the sub-flywheel in the wheel rotational direction restricted. However, when the radial position of the center of gravity of the weight increases, the pressing force on the main flywheel or a member rotating together with the main flywheel decreases. A variable inertia flywheel characterized by comprising: a contact portion that interlocks to move the center of gravity, and a spring member that biases the weight in a direction in which the radial position of the center of gravity decreases. 2) The main flywheel is brought into contact with the cylindrical or conical inner surface of the main flywheel or a member that rotates together with the main flywheel by a contact part that is in an interlocking relationship with the sub flywheel or a weight that rotates together with the sub flywheel. The flywheel and the auxiliary flywheel are configured to transmit rotational force to each other, and the swinging fulcrum of the weight is located at an intermediate position in the rotational direction between the point of application from the weight to the contact portion and the center of gravity of the weight. A variable inertia flywheel according to claim 1, characterized in that:
JP63002249A 1988-01-08 1988-01-08 Variable inertial moment flywheel Pending JPH01182651A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP63002249A JPH01182651A (en) 1988-01-08 1988-01-08 Variable inertial moment flywheel

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP63002249A JPH01182651A (en) 1988-01-08 1988-01-08 Variable inertial moment flywheel

Publications (1)

Publication Number Publication Date
JPH01182651A true JPH01182651A (en) 1989-07-20

Family

ID=11524081

Family Applications (1)

Application Number Title Priority Date Filing Date
JP63002249A Pending JPH01182651A (en) 1988-01-08 1988-01-08 Variable inertial moment flywheel

Country Status (1)

Country Link
JP (1) JPH01182651A (en)

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2736120A1 (en) * 1995-06-27 1997-01-03 Valeo DOUBLE DAMPER FLYWHEEL, IN PARTICULAR FOR MOTOR VEHICLES
WO2004063593A3 (en) * 2003-01-14 2004-09-16 Safe Developments Ltd Flywheel with pendulum masses
JP2009162285A (en) * 2007-12-28 2009-07-23 Yamaha Motor Co Ltd Centrifugal clutch, engine unit, and straddle type vehicle
JP2015036521A (en) * 2013-08-12 2015-02-23 株式会社シンプル東京 Revolution retainer
WO2016047789A1 (en) * 2014-09-25 2016-03-31 アイシン・エィ・ダブリュ株式会社 Damper device
US9958051B2 (en) 2014-10-29 2018-05-01 Borgwarner Inc. Torsionally compliant sprocket with locking mechanism

Cited By (9)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
FR2736120A1 (en) * 1995-06-27 1997-01-03 Valeo DOUBLE DAMPER FLYWHEEL, IN PARTICULAR FOR MOTOR VEHICLES
WO2004063593A3 (en) * 2003-01-14 2004-09-16 Safe Developments Ltd Flywheel with pendulum masses
JP2009162285A (en) * 2007-12-28 2009-07-23 Yamaha Motor Co Ltd Centrifugal clutch, engine unit, and straddle type vehicle
EP2075481A3 (en) * 2007-12-28 2013-04-24 Yamaha Hatsudoki Kabushiki Kaisha Centrifugal clutch
JP2015036521A (en) * 2013-08-12 2015-02-23 株式会社シンプル東京 Revolution retainer
WO2016047789A1 (en) * 2014-09-25 2016-03-31 アイシン・エィ・ダブリュ株式会社 Damper device
KR20170041823A (en) * 2014-09-25 2017-04-17 아이신에이더블류 가부시키가이샤 Damper device
JPWO2016047789A1 (en) * 2014-09-25 2017-06-08 アイシン・エィ・ダブリュ株式会社 Damper device
US9958051B2 (en) 2014-10-29 2018-05-01 Borgwarner Inc. Torsionally compliant sprocket with locking mechanism

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