JPH05240300A - Flexible coupling - Google Patents
Flexible couplingInfo
- Publication number
- JPH05240300A JPH05240300A JP3060968A JP6096891A JPH05240300A JP H05240300 A JPH05240300 A JP H05240300A JP 3060968 A JP3060968 A JP 3060968A JP 6096891 A JP6096891 A JP 6096891A JP H05240300 A JPH05240300 A JP H05240300A
- Authority
- JP
- Japan
- Prior art keywords
- spring
- elastic
- springs
- joint according
- elastic joint
- 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
- 230000008878 coupling Effects 0.000 title claims abstract description 14
- 238000010168 coupling process Methods 0.000 title claims abstract description 14
- 238000005859 coupling reaction Methods 0.000 title claims abstract description 14
- 230000005489 elastic deformation Effects 0.000 claims abstract description 4
- 238000004804 winding Methods 0.000 claims description 6
- 238000002485 combustion reaction Methods 0.000 claims description 3
- 239000000314 lubricant Substances 0.000 claims description 3
- 230000004323 axial length Effects 0.000 claims description 2
- 230000002093 peripheral effect Effects 0.000 claims description 2
- 230000006835 compression Effects 0.000 abstract 1
- 238000007906 compression Methods 0.000 abstract 1
- 238000010276 construction Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 239000000470 constituent Substances 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
- 238000004519 manufacturing process Methods 0.000 description 1
- 238000005096 rolling process Methods 0.000 description 1
- 239000003566 sealing material Substances 0.000 description 1
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
- F16F15/131—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 rotating system comprising two or more gyratory masses
- F16F15/133—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 rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/134—Wound springs
- F16F15/1343—Wound springs characterised by the spring mounting
- F16F15/13438—End-caps for springs
-
- 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
- F16F15/131—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 rotating system comprising two or more gyratory masses
- F16F15/133—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 rotating system comprising two or more gyratory masses using springs as elastic members, e.g. metallic springs
- F16F15/134—Wound springs
- F16F15/13469—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations
- F16F15/13476—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates
- F16F15/13484—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs
- F16F15/13492—Combinations of dampers, e.g. with multiple plates, multiple spring sets, i.e. complex configurations resulting in a staged spring characteristic, e.g. with multiple intermediate plates acting on multiple sets of springs the sets of springs being arranged at substantially the same radius
Landscapes
- Engineering & Computer Science (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Acoustics & Sound (AREA)
- Aviation & Aerospace Engineering (AREA)
- Mechanical Engineering (AREA)
- Mechanical Operated Clutches (AREA)
- Springs (AREA)
- Arrangement Or Mounting Of Propulsion Units For Vehicles (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】この発明は、請求項１の上位概
念、すなわち、特に内燃機関の分割型はずみ車に適する
円板構造の弾性継手であって、相対的に回動可能な２つ
の継手半体(１)(２)を備えており、この継手半体(１)
(２)の周囲には、互いに分離された複数の切抜き孔(６)
があけられ、各切抜き孔(６)内に、弾性的な継手要素が
配置されており、この弾性的な継手要素は、好ましくは
直列に接続されたコイルばねとして構成されていて、２
つの継手半体(１)(２)相互の回動に際して、順々に作用
するようになっているものに関する。この種の継手は、
日本国特開昭61-290235号公報に開示されている。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to the general concept of claim 1, that is, an elastic joint having a disc structure, which is particularly suitable for a split type flywheel of an internal combustion engine. It has a body (1) (2), and this joint half (1)
Around the circumference of (2), a plurality of cutout holes (6) separated from each other.
And in each cutout hole (6) an elastic coupling element is arranged, which elastic coupling element is preferably configured as a series connected coil spring,
The present invention relates to one that is adapted to act in order when the two joint halves (1) and (2) rotate relative to each other. This kind of fitting
It is disclosed in Japanese Patent Laid-Open No. 61-290235.
【０００２】[0002]
【従来の技術】このような構成の継手は、内燃機関の回
転のむらを、後続の駆動軸に伝えないようにするため
の、いわゆる２重質量はずみ車でもある。弾性の継手要
素の弾性率を適正に設定すれば、駆動軸系全体の運転特
性又は共振特性に影響を及ぼさすことができる。2. Description of the Related Art A joint having such a structure is also a so-called double-mass flywheel for preventing uneven rotation of an internal combustion engine from being transmitted to a drive shaft that follows. By properly setting the elastic modulus of the elastic joint element, it is possible to affect the operating characteristics or resonance characteristics of the entire drive shaft system.
【０００３】この種の２重質量はずみ車自体は、***国
特許発明第3708345号明細書(欧州特許公開第7902828.8
号)に開示されている。この継手は、３種類の異なる剛
性のばねを有しており、この剛性は、それぞれある特定
の運転領域に関係付けられている。比較的弱いばねは、
小さなトルクのアイドリング段階でのみ作用し、第２ば
ねは、主運転領域を受け持ち、第３のばねは、トルクピ
ーク発生時のストッパーとして作用する。This kind of double-mass flywheel itself is described in West German Patent Invention No. 3708345 (European Patent Publication No. 7902828.8).
No.). The joint has three different stiffness springs, each stiffness being associated with a particular operating region. Relatively weak springs
Acting only in the small torque idling stage, the second spring is responsible for the main operating region and the third spring acts as a stopper during torque peaks.
【０００４】全てのばねは、窓形状の切り抜き孔内に配
設されており、各切抜き孔内には、１つのばねだけが組
み込まれている。すなわち、継手は多数の窓を有してい
るため、その製作が面倒である。All springs are arranged in window-shaped cutouts, with only one spring being installed in each cutout. That is, since the joint has many windows, its manufacture is troublesome.
【０００５】これに対して、特開昭61-290235号公報に
開示されたものは、３つのばねからなる１つのばねユニ
ットが、窓形の切抜き孔内にそれぞれ組み込まれてい
る。この場合、各ばねは、力の伝達に関して直列的に接
続されており、相互にほぼ同じ長さの通常コイルばねが
用いられている。On the other hand, according to the one disclosed in Japanese Patent Laid-Open No. 61-290235, one spring unit composed of three springs is incorporated in each window-shaped cutout hole. In this case, the springs are connected in series with respect to the transmission of force, and normal coil springs of approximately the same length as one another are used.
【０００６】したがって、ばねの省略又追加によるばね
特性の変更は、切抜き孔の形状を変えなければ不可能で
ある。その上にこれらのばねの寿命を延ばそうとすれ
ば、過度に圧縮されないようにしなければならない。し
かしこれは面倒なことである。Therefore, it is impossible to change the spring characteristics by omitting or adding a spring unless the shape of the cutout hole is changed. In addition, if one wishes to extend the life of these springs, one must ensure that they are not over-compressed. But this is a hassle.
【０００７】[0007]
【発明が解決しようとする課題】本発明の課題は、アイ
ドリング運転に関与するばね(アイドリングばね)の破損
のおそれがまったくなく、しかも、切抜き孔の形状を変
更しなくても(アイドリング段階を含むか又は含まな
い)、ばね特性を変更することができるように、アイド
リングばねと主運転領域用のばね(主ばね)とが構成され
ている、前記形式の弾性継手を提供することにある。SUMMARY OF THE INVENTION An object of the present invention is to eliminate the risk of damage to a spring (idling spring) involved in idling operation and to change the shape of the cutout hole (including the idling step). (Or not including), an elastic joint of the type described above, in which an idling spring and a spring for the main operating region (main spring) are configured so that the spring characteristics can be changed.
【０００８】[0008]
【課題を解決するための手段】この課題は請求項１に記
載の特徴事項によって解決される。すなわち、２つのば
ねが、窓形状の切抜き孔内でばねブロックとして直列に
接続されており、アイドリングばねの長さ、すなわち、
軸方向の長さは、主ばねの長さと比べて極めて短かい。
これは、周方向のほとんどの空間を、主ばねのために利
用することができるという利点を有する。This problem is solved by the features of claim 1. That is, the two springs are connected in series as a spring block in a window-shaped cutout, the length of the idling spring, ie,
The axial length is extremely short compared to the length of the main spring.
This has the advantage that most of the circumferential space is available for the main spring.
【０００９】また、継手の構成を変えることなく、アイ
ドリング段階を含むか又は含まない種々のばね特性を実
現することが可能である。これは、主ばねを、アイドリ
ングばねも含めてほんの僅かに長い主ばねと交換するこ
とにより達成される。It is also possible to realize various spring characteristics with or without idling steps, without changing the configuration of the joint. This is achieved by replacing the main spring with a slightly longer main spring, including the idling spring.
【００１０】さらに、アイドリング運転に関与するバネ
は、２つの継手半体相互の回動角度の初期の範囲のみで
有効に作用するような、非常に小さな剛性を有してい
る。Furthermore, the springs involved in idling operation have a very small rigidity such that they act effectively only in the initial range of the rotation angle between the two coupling halves.
【００１１】またこのばねは、最大の伝達可能なトルク
を超過すると直ちに、巻き部分が、平面的に圧縮される
ように構成されている。これは、巻き部分が互いに位置
ずれしたり、歪みを生じるたりすることがないため、ア
イドリングばねが過度に圧縮されないように保護する必
要がないとう利点を有する。The spring is also designed in such a way that the winding section is compressed in plane as soon as the maximum transmissible torque is exceeded. This has the advantage that it is not necessary to protect the idling spring from being over-compressed, as the windings will not be displaced relative to each other or be distorted.
【００１２】前記の特徴により、最小コストでばね特性
の構成が可能となり、したがって、簡単な継手の利用範
囲は拡大する。The above features allow construction of spring properties at a minimum cost, thus expanding the range of applications for simple joints.
【００１３】請求項２以下は、本発明の有利な構成を示
している。請求項２によれば、アイドリング運転に関与
するばねとして、１回巻かれただけのばねを選択してい
る。このばねは、最大行程時に、ワイヤの太さに相当す
る厚さしか有しない。Claims 2 and below show advantageous configurations of the invention. According to claim 2, as the spring involved in the idling operation, the spring which is wound once is selected. This spring has a thickness corresponding to the thickness of the wire at the maximum stroke.
【００１４】請求項３によれば、このばねを円錐ばねと
して構成している。この円錐ばねの各巻き部分は、完全
に圧縮された時に、渦巻き状に半径方向に入り込む。請
求項４及び５によれば、各ばねの中間に、平坦な円板と
して構成された１つの分離要素がそれぞれ設けられてい
る。According to the third aspect, this spring is constructed as a conical spring. The windings of this conical spring spiral in radially when fully compressed. According to claims 4 and 5, in the middle of each spring there is provided in each case one separating element configured as a flat disc.
【００１５】請求項６によれば、各ブロックは、２つの
継手半体の各切抜き孔内で、ばね受けによってセンタリ
ングされて案内されている。請求項７によれば、円錐ば
ねを選択した場合には、この円錐ばねは、その大直径部
をもって、一方のばね受けの内周面によって案内される
ように組み込まれている。この場合、円錐ばねの大直径
部は、主運転領域内の他方のばねに向けられている。According to the sixth aspect, each block is guided by being centered by the spring bearing in each cutout hole of the two joint halves. According to claim 7, when a conical spring is selected, this conical spring is integrated with its large diameter part so as to be guided by the inner peripheral surface of one of the spring bearings. In this case, the large diameter portion of the conical spring is oriented towards the other spring in the main operating area.
【００１６】請求項８によれば、継手内部に液密性の内
部空間が形成されている。この内部空間を粘性媒体で満
たすことができ、この粘性媒体は、ばねブロックに潤滑
剤を常時供給している。According to the eighth aspect, a liquid-tight internal space is formed inside the joint. This internal space can be filled with a viscous medium, which constantly supplies the spring block with lubricant.
【００１７】[0017]
【実施例】本発明を、以下、実施例を示す図面に基づい
て、より詳細に説明する。図１及び図２には、ころがり
軸受(３)を介して相互に支承された２つの継手半体(１)
(２)を有する弾性継手が示されている。The present invention will be described in more detail below with reference to the drawings showing an embodiment. 1 and 2 show two coupling halves (1), which are mutually supported by means of rolling bearings (3).
An elastic joint with (2) is shown.
【００１８】第２の継手半体(２)は中間円板(４)を支持
しており、同中間円板(４)は、継手半体(２)の２つの側
方円板(５)によって形成された内部空間内で回動可能で
ある。The second joint half (2) carries an intermediate disc (4) which comprises the two side discs (5) of the joint half (2). It is rotatable in the internal space formed by.
【００１９】中間円板(４)も側方円板(５)も、本質的に
同形の切抜き孔(６)を有しており、同切抜き孔(６)内に
は、ばねブロック(７)が配設されている。この構成によ
って、それ自体としては公知の方式で、第１の継手半体
(１)から第２の継手半体(２)にトルクが伝達される。こ
の場合、周方向の力は、それぞればね受け(８)(９)を介
して、ばねブロック(７)の両端部に作用している。Both the intermediate disc (4) and the side discs (5) have essentially the same cutouts (6), in which the spring blocks (7) are located. Are arranged. Due to this construction, in a manner known per se, the first coupling half is
Torque is transmitted from (1) to the second joint half (2). In this case, the circumferential force acts on both ends of the spring block (7) via the spring bearings (8) and (9), respectively.
【００２０】図３は、図１の切断線III−IIIに沿ったば
ねブロックの詳細断面図である。図３から、第１の継手
半体(１)における側方円板(５)と第２継手半体(２)にお
ける中間円板(４)が認められる。FIG. 3 is a detailed cross-sectional view of the spring block taken along section line III-III in FIG. From FIG. 3 a side disc (5) in the first joint half (1) and an intermediate disc (4) in the second joint half (2) can be seen.
【００２１】中間円板(４)と側方円板(５)における同形
の切抜き孔(６)内にばねブロック(７)が、両側にばね受
け(８)(９)を介在させて組み込まれている。ばねブロッ
ク(７)は、２つのばね、すなわち第１のばね(11)と第２
のばね(12)を含んでいる。Spring blocks (7) are installed in the same shaped cut-out holes (6) in the intermediate disc (4) and the side discs (5) with spring bearings (8) and (9) interposed on both sides. ing. The spring block (7) has two springs, the first spring (11) and the second spring.
Includes spring (12).
【００２２】周方向の力を、一方の継手半体からばね受
けに伝達し、さらに同ばね受けから直列に配列された各
ばね(11)(12)に伝達するために、両ばね(11)(12)の中
間、並びに場合によっては、各ばね(11)(12)の互いに離
反する端面側にも、円形の分離要素としての円板(14)が
設けられている。In order to transmit the force in the circumferential direction from one of the joint halves to the spring bearing, and further from the spring bearing to each spring (11) (12) arranged in series, both springs (11) A disc (14) serving as a circular separating element is provided in the middle of (12) and, as the case may be, also on the end face sides of the springs (11) and (12) which are separated from each other.
【００２３】第１のばね(11)は、１巻きのばねとして構
成されており、第２のばね(12)は、複数の巻き数を有し
ている。第１のばね(11)の剛性は、第２のばね(12)の剛
性よりも本質的に小さい。The first spring (11) is constructed as a one-turn spring and the second spring (12) has a plurality of turns. The stiffness of the first spring (11) is essentially less than the stiffness of the second spring (12).
【００２４】このようなばねブロック(７)の各ばね(11)
(12)の配置に基づいて、小トルクに際しては、回動角度
の大部分は第１のばね(11)によってもたらされる。何故
なら、他方のばね(12)は、比較的大きな剛性を有してお
り、したがって、小トルクに際しては、ほんの僅かしか
弾性変形しないからである。Each spring (11) of such a spring block (7)
Due to the arrangement of (12), during small torques most of the pivoting angle is provided by the first spring (11). This is because the other spring (12) has a relatively large rigidity, and therefore elastically deforms only slightly at a small torque.
【００２５】１巻きのばねが、２つの円板(14)の間に挾
まれて平面化した時に衝突が発生する。トルクが増加し
続けると、今度は第２のばね(12)が、その最大の弾性変
形に至るまで、引き続く回動角度の大部分を引き受ける
ようになる。A collision occurs when one turn of the spring is sandwiched between the two discs (14) and planarized. As the torque continues to increase, the second spring (12) in turn will take up most of the subsequent pivot angle until it reaches its maximum elastic deformation.
【００２６】こうして、第１のばね(11)は、特に原動機
のアイドリング運転に関与し、第２のばね(12)は、原動
機の主運転領域に関与することになる。第１のばね(11)
は、周方向における長さが短いため、主運転領域に関与
している第２のばね(12)の寸法にはほとんど影響を及ぼ
さない。したがって、主運転領域に関与している第２の
ばね(12)の寸法のみが、事実上、切抜き孔(６)内の構成
空間を占めている。Thus, the first spring (11) is particularly involved in idling operation of the prime mover, and the second spring (12) is involved in the main operating area of the prime mover. First spring (11)
Has a small circumferential length and therefore has little effect on the dimensions of the second spring (12) involved in the main operating region. Therefore, only the dimensions of the second spring (12), which are responsible for the main operating area, occupy virtually the constituent space within the cutout (6).
【００２７】ばねブロック(７)として統合された各ばね
(11)(12)は、分離円板(14)も含めて常に互いに同軸的な
状態を正確に維持するべく、ばね受け(８)(９)によって
案内されている。Each spring integrated as a spring block (7)
The (11) and (12) are guided by the spring bearings (8) and (9) so as to always maintain the correct state of being coaxial with each other, including the separating disc (14).
【００２８】そのため、一方のばね受け(８)はスリーブ
形状であって、その中で、ばね(12)及び相応の分離円板
(14)が、外側からセンタリングされている。これに対し
て、ばね受け(９)は、心棒によって、ばね(11)(12)をそ
の内径に関してセンタリングしている。To that end, one spring bearing (8) is sleeve-shaped, in which the spring (12) and the corresponding separating disc are
(14) is centered from the outside. In contrast, the spring bearing (9) centers the springs (11) and (12) with respect to their inner diameter by means of a mandrel.
【００２９】ばねブロック(７)の１つの切抜き孔(６)内
に、外側でセンタリングするためのばね受け(８)を２個
配置することも、内側でセンタリングするためのばね受
け(９)を２個配置することも、をあるいはそれらを組合
わせて配置することも可能である。It is also possible to arrange two spring bearings (8) for centering on the outside in one cutout hole (6) of the spring block (7) or to arrange spring bearings (9) for centering on the inside. It is also possible to arrange two, or to arrange them in combination.
【００３０】外側でセンタリングするためのばね受け
(８)を２個組み込んだ場合、その互いに向かい合う端面
を、回動角度ストッパーとして構成することができる。
この場合には、ばねブロック(７)の各ばね(11)(12)が、
このストッパー機能を引き受ける必要はない。Spring bearing for centering on the outside
When two (8) are incorporated, the end faces facing each other can be configured as a rotation angle stopper.
In this case, each spring (11) (12) of the spring block (7)
It is not necessary to undertake this stopper function.
【００３１】これに代わって、内側でセンタリングする
ためのばね受け(９)を２個使用した場合には、互いに向
かい合っている心棒を、回動角度ストッパーとして構成
することができる。Alternatively, if two spring bearings (9) for centering on the inside are used, the mandrels facing each other can be constructed as pivot angle stoppers.
【００３２】外側または内側でセンタリングするための
ばね受けを組み合わせて使用する場合には、内側でセン
タリングするためのばね受け(９)のスリーブ状の外側部
分も、また回動角度ストッパーとして構成すると有利で
ある。When using a combination of spring bearings for centering on the outside or the inside, it is advantageous if the sleeve-shaped outer part of the spring bearing (9) for centering on the inside is also configured as a pivot angle stop. Is.
【００３３】図４は、本質的に１回巻かれただけの１巻
きばね(11)を示している。このばね(11)は、ばね端部の
引っ掛かりを避けて、ばね受け内部での、もしくは分離
円板(14)への正確な密着を保証するために、360゜以下
の巻回領域を有している。FIG. 4 shows a one-turn spring (11) which is essentially only wound once. This spring (11) has a winding area of 360 ° or less in order to avoid catching of the spring end and to ensure accurate contact inside the spring receiver or to the separating disc (14). ing.
【００３４】図５は、第１のばねが円錐ばね(11a)とし
て構成されいる場合のばねブロック(７)を示している。
この円錐ばね(11a)は、周方向の比較的長い距離をも橋
渡しすることができるという利点を有する。この場合、
円錐形状は、ワイヤの１巻き分の厚さに相当する長さま
で圧縮することができるように選択されている。FIG. 5 shows the spring block (7) when the first spring is constructed as a conical spring (11a).
This conical spring (11a) has the advantage that it can bridge a relatively long distance in the circumferential direction. in this case,
The conical shape is selected so that it can be compressed to a length corresponding to the thickness of one turn of wire.
【００３５】ユニット化によって、ばね受け(８)(９)の
間に様々な形態のばねを組み込むことができる。ある特
定の使用目的から、１つのばねだけを使用する場合に
は、公知のように、図６に示すような特性曲線が得られ
る。回動角度Ｗにわたって、トルクＭは本質的に直線的
に増加している。Due to the unitization, various types of springs can be incorporated between the spring bearings (8) and (9). In the case of using only one spring for a particular purpose of use, a characteristic curve as shown in FIG. 6 is obtained, as is known. Over the turning angle W, the torque M increases essentially linearly.
【００３６】図７は、２種類のばねが、１つのばねブロ
ック(７)に統合されいる場合の継手を示している。そこ
では、折れ曲がった特性曲線が生じている。この場合、
比較的小さな回動角度領域ａは、１巻きの短いばね(11)
に対応している。同回動角度領域ａには、複数回巻かれ
た比較的大きな剛性の第２のばねに対応する回動角度領
域ｂが続いている。FIG. 7 shows the joint when two types of springs are integrated in one spring block (7). There is a bent characteristic curve. in this case,
The relatively small turning angle area a has a short turn of one turn (11).
It corresponds to. The rotation angle region a is followed by the rotation angle region b corresponding to the second spring that is wound a plurality of times and has a relatively large rigidity.
【００３７】図２から、側方円板(５)によって取り囲ま
れた内部空間は、ケーシングの半径方向外側に対して
も、半径方向内側に対しても、シール材によって密封さ
れていることがわかる。From FIG. 2 it can be seen that the internal space surrounded by the side circular plate (5) is sealed by the sealing material both on the radially outer side and the radially inner side of the casing. ..
【００３８】また、密閉された媒体によって有効に作用
する緩衝手段を、継手に設けることができる。この場
合、密閉された媒体は、同時に、密閉されたばねブロッ
クに潤滑剤を供給して、磨耗を防止する。In addition, the joint may be provided with a cushioning means that works effectively with the sealed medium. In this case, the sealed medium simultaneously supplies a lubricant to the sealed spring block to prevent wear.
【図１】継手のばねブロックの領域の横断面図である。1 is a cross-sectional view in the region of a spring block of a joint.
【図２】継手の断面図である。FIG. 2 is a sectional view of a joint.
【図３】２つのばねを組み合わせたばねブロックの縦断
面図である。FIG. 3 is a vertical cross-sectional view of a spring block in which two springs are combined.
【図４】１巻きばねの側面図である。FIG. 4 is a side view of a single-winding spring.
【図５】円錐ばねとしての第１のばねを有するばねブロ
ックの縦断面図である。FIG. 5 is a vertical cross-sectional view of a spring block having a first spring as a conical spring.
【図６】可能なばね特性のグラフである。FIG. 6 is a graph of possible spring characteristics.
【図７】可能なばね特性のグラフである。FIG. 7 is a graph of possible spring characteristics.
(１)(２)継手半体 (３)軸受 (４)中間円板 (５)側方円
板 (６)切抜き孔 (７)ばねブ
ロック (８)(９)ばね受け (11)(12)ば
ね (11a)円錐ばね (14)円板(1) (2) Joint half (3) Bearing (4) Intermediate disk (5) Side disk (6) Cutout hole (7) Spring block (8) (9) Spring bearing (11) (12) Spring (11a) Conical spring (14) Disc
Claims (8)
円板構造の弾性継手であって、相対的に回動可能な２つ
の継手半体(１)(２)を備えており、この継手半体(１)
(２)の周囲には、互いに分離された複数の切抜き孔(６)
があけられ、各切抜き孔(６)内に、弾性的な継手要素が
配置されており、この弾性的な継手要素は、好ましくは
直列に接続されたコイルばねとして構成されていて、２
つの継手半体(１)(２)相互の回動に際して、順々に作用
するようになっているものにおいて、 (a) 弾性的な継手要素は、２つのばね(11)(12)からなる
１つのばねブロック(７)に統合されており、 (b) これらのばね(11)(12)は、異なる剛性を有してい
て、第１のばね(11)は、第２のばね(12)よりも本質的に
小さな剛性を有しており、その結果、第１のばね(11)
は、原動機のアイドル運転に関与し、第２のばね(12)
は、原動機の主運転に関与しており、 (c) 第１のばね(11)は、原動機のアイドリングトルク以
上のトルクによる最大弾性変形に際して圧縮され、かつ
ばねブロック(７)内での軸方向長が、１巻き分の厚さに
相当するように構成されており、 (d) 第１のばね(11)は、第２のばね(12)よりも本質的に
小さな軸方向長さを有していることを特徴とする弾性継
手。1. An elastic joint having a disc structure particularly suitable for a split type flywheel of an internal combustion engine, comprising two relatively rotatable joint halves (1) and (2). Body (1)
Around the circumference of (2), a plurality of cutout holes (6) separated from each other.
And in each cutout hole (6) an elastic coupling element is arranged, which elastic coupling element is preferably configured as a series connected coil spring,
(A) The elastic coupling element consists of two springs (11) (12), in which the two coupling halves (1) (2) are adapted to act in turn upon mutual rotation. Integrated in one spring block (7), (b) these springs (11) (12) have different stiffness, the first spring (11) is the second spring (12) ) Essentially less than that of the first spring (11)
Is involved in the idle operation of the prime mover, the second spring (12)
Is involved in the main operation of the prime mover, and (c) the first spring (11) is compressed during the maximum elastic deformation due to a torque equal to or greater than the idling torque of the prime mover, and the axial direction within the spring block (7). The length is configured to correspond to the thickness of one turn, and (d) the first spring (11) has an axial length that is substantially smaller than that of the second spring (12). An elastic joint characterized in that
ただけの１巻きばねとして構成されている請求項１記載
の弾性継手。2. Elastic joint according to claim 1, characterized in that the first spring (11) is constructed essentially as a one-turn spring which is wound only once.
て構成されており、その各巻き部分は、最大弾性変形に
際して渦巻き状に半径方向に入り込んで平面的に圧縮さ
れるようになっている請求項１記載の弾性継手。3. The first spring (11) is constructed as a conical spring (11a), each winding part of which is adapted to spirally enter a radial direction during maximum elastic deformation and to be planarly compressed. The elastic joint according to claim 1, wherein
の分離要素(14)が挿入されている請求項１ないし３のい
ずれかに記載の弾性継手。4. The elastic joint according to claim 1, wherein one separating element (14) is inserted in the middle of each spring (11) (12).
されている請求項４記載の弾性継手。5. Elastic joint according to claim 4, characterized in that the separating element (14) is constructed as an annular disc.
(６)内において、各ばねブロック(７)が、ばね受け(８)
(９)によってセンタリングされて案内されている請求項
１ないし５のいずれかに記載の弾性継手。6. Cut-out holes in two joint halves (1) (2)
In (6), each spring block (7) has a spring bearing (8).
The elastic joint according to any one of claims 1 to 5, which is centered and guided by (9).
のばね(12)の方に向けて組み込まれており、各円錐ばね
(11a)は、一方のばね受け(８)の内周面によって案内さ
れている請求項３ないし６のいずれかに記載の弾性継
手。7. The conical spring (11a) has a second large diameter portion.
Mounted towards the springs (12) of each conical spring
The elastic joint according to any one of claims 3 to 6, wherein the (11a) is guided by the inner peripheral surface of one spring bearing (8).
よって構成され、かつ粘性媒体で満たされた液密性の内
部空間を有しており、この内部空間内で、ばねブロック
(７)に潤滑剤が常時供給されている請求項１ないし７の
いずれかに記載の弾性継手。8. The first half-body joint (1) comprises a lateral disc (5) and has a liquid-tight internal space filled with a viscous medium. And the spring block
The elastic joint according to any one of claims 1 to 7, wherein the lubricant is constantly supplied to (7).
Applications Claiming Priority (2)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| DE4006685 | 1990-03-03 | ||
| DE4006685.1 | 1990-03-03 |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH05240300A true JPH05240300A (en) | 1993-09-17 |
| JP2904313B2 JP2904313B2 (en) | 1999-06-14 |
Family
ID=6401345
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP3060968A Expired - Lifetime JP2904313B2 (en) | 1990-03-03 | 1991-03-04 | Elastic joint |
Country Status (4)
| Country | Link |
|---|---|
| JP (1) | JP2904313B2 (en) |
| FR (1) | FR2659120B1 (en) |
| GB (1) | GB2241560B (en) |
| IT (1) | IT1245429B (en) |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20010049980A (en) * | 1999-08-10 | 2001-06-15 | 가이스링거 마티아스 | Torsionally flexible coupling |
| JP2019049286A (en) * | 2017-09-08 | 2019-03-28 | アイシン精機株式会社 | damper |
Families Citing this family (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE4128868A1 (en) * | 1991-08-30 | 1993-03-04 | Fichtel & Sachs Ag | TWO-MASS FLYWHEEL WITH SLIDE SHOE |
| US5511446A (en) * | 1991-09-04 | 1996-04-30 | Kabushiki Kaisha Daikin Seisakusho | Flywheel assembly |
| US5355747A (en) * | 1991-09-04 | 1994-10-18 | Kabushiki Kaisha Daikin Seisakusho | Flywheel assembly |
| DE4235519C2 (en) * | 1991-10-21 | 2002-03-21 | Exedy Corp | flywheel training |
| DE19830432A1 (en) | 1998-07-08 | 2000-01-13 | Rohs Voigt Patentverwertungsge | Process for damping torsional vibrations and torsional vibration damper |
| FR2795471B1 (en) * | 1999-06-22 | 2003-02-21 | Mannesmann Sachs Ag | SUPPORT ELEMENT FOR TORSIONAL OSCILLATOR AND DAMPER THUS PRODUCED |
| TR201505304A2 (en) * | 2015-04-30 | 2015-07-21 | Valeo Otomotiv Sanayi Ve Ticaret A S | A POWER TRANSMISSION ARRANGEMENT WITH DRIVE PLATE |
| FR3057322B1 (en) * | 2016-10-06 | 2018-11-09 | Peugeot Citroen Automobiles Sa | DOUBLE ENGINE FLYWHEEL COMPRISING HYDRAULIC SHOCKS |
Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61170723U (en) * | 1985-04-11 | 1986-10-23 | ||
| JPH0165936U (en) * | 1987-10-21 | 1989-04-27 | ||
| JPH01149024U (en) * | 1988-04-05 | 1989-10-16 |
Family Cites Families (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61290235A (en) * | 1985-06-15 | 1986-12-20 | Hino Motors Ltd | Clutch disc |
| GB2214610B (en) * | 1988-01-29 | 1991-09-25 | Luk Lamellen & Kupplungsbau | Flywheel |
| DE3937957A1 (en) * | 1988-12-15 | 1990-06-21 | Voith Gmbh J M | ELASTIC COUPLING |
-
1991
- 1991-03-01 GB GB9104353A patent/GB2241560B/en not_active Expired - Fee Related
- 1991-03-01 FR FR9102464A patent/FR2659120B1/en not_active Expired - Fee Related
- 1991-03-01 IT ITTO910146A patent/IT1245429B/en active IP Right Grant
- 1991-03-04 JP JP3060968A patent/JP2904313B2/en not_active Expired - Lifetime
Patent Citations (3)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS61170723U (en) * | 1985-04-11 | 1986-10-23 | ||
| JPH0165936U (en) * | 1987-10-21 | 1989-04-27 | ||
| JPH01149024U (en) * | 1988-04-05 | 1989-10-16 |
Cited By (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20010049980A (en) * | 1999-08-10 | 2001-06-15 | 가이스링거 마티아스 | Torsionally flexible coupling |
| JP2019049286A (en) * | 2017-09-08 | 2019-03-28 | アイシン精機株式会社 | damper |
Also Published As
| Publication number | Publication date |
|---|---|
| JP2904313B2 (en) | 1999-06-14 |
| GB9104353D0 (en) | 1991-04-17 |
| FR2659120A1 (en) | 1991-09-06 |
| ITTO910146A0 (en) | 1991-03-01 |
| IT1245429B (en) | 1994-09-20 |
| ITTO910146A1 (en) | 1992-09-01 |
| GB2241560A (en) | 1991-09-04 |
| GB2241560B (en) | 1993-09-08 |
| FR2659120B1 (en) | 1993-10-29 |
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