JP2017057924A

JP2017057924A - Rotation transmission device

Info

Publication number: JP2017057924A
Application number: JP2015183122A
Authority: JP
Inventors: 齋藤　隆英; Takahide Saito; 隆英齋藤; 川合　正浩; Masahiro Kawai; 正浩川合
Original assignee: NTN Corp; NTN Toyo Bearing Co Ltd
Current assignee: NTN Corp
Priority date: 2015-09-16
Filing date: 2015-09-16
Publication date: 2017-03-23

Abstract

PROBLEM TO BE SOLVED: To attenuate generated rotation pulsation, regardless of a rotational frequency of a driving device such as an engine.SOLUTION: Used is a rotation transmission device including a variable mechanism for a spring constant of an elastic member, in which at least two elastic members are inserted into a structural member configured to transmit rotation from an input shaft, and which acts on the structural member according to change of a rotational frequency of the input shaft.SELECTED DRAWING: Figure 1(b)

Description

本発明は、回転伝達装置に関し、詳しくは、少なくとも２つの弾性部材を用い、回転脈動を減衰可能とする回転伝達装置に関する。 The present invention relates to a rotation transmission device, and more particularly, to a rotation transmission device that uses at least two elastic members and can attenuate rotational pulsation.

エンジン等の駆動装置からの回転を伝達する際において、同時に発生する回転脈動を除去する機構として、例えば特許文献１に示されているような、プーリの内径側に環状の湾曲ばねを挿置し、この湾曲ばねによって脈動を減衰させて、回転のみを補機類に伝達する回転伝達機構が知られている。 As a mechanism for removing rotational pulsations that occur simultaneously when transmitting rotation from a drive device such as an engine, an annular curved spring is inserted on the inner diameter side of a pulley as shown in Patent Document 1, for example. A rotation transmission mechanism is known in which the pulsation is attenuated by the curved spring and only rotation is transmitted to the auxiliary machinery.

特表２０１３−５１９１２９号公報Special table 2013-519129 gazette

しかしながら、前記特許文献１に記載の機構は、１つの湾曲ばねを用いており、エンジン等の駆動装置の低回転において生じる回転脈動を減衰しようとすると、当該湾曲ばねのばね定数を低くする必要がある。しかし、ばね定数を低くすると、固定振動数が低下することとなり、エンジン等の駆動装置が高回転となった際に共振が発生しやすくなる。
一方、この共振の発生を抑制するため、ばね定数を比較的高めに設定すると、エンジン等の駆動装置の低回転域での回転脈動を十分に減衰できなくなるという問題点を有する。 However, the mechanism described in Patent Document 1 uses one curved spring, and it is necessary to reduce the spring constant of the curved spring in order to attenuate the rotational pulsation that occurs when the drive device such as the engine rotates at a low speed. is there. However, when the spring constant is lowered, the fixed frequency is lowered, and resonance is likely to occur when a drive device such as an engine is rotated at a high speed.
On the other hand, if the spring constant is set relatively high in order to suppress the occurrence of this resonance, there is a problem that the rotational pulsation in the low rotation range of the drive device such as the engine cannot be sufficiently attenuated.

そこで、この発明は、エンジン等の駆動装置の回転数の高低に関わらず、生じる回転脈動を減衰させることを目的とする。 Therefore, an object of the present invention is to attenuate the generated rotational pulsation regardless of the rotational speed of a driving device such as an engine.

上記の課題を解決するために、この発明は、入力軸からの回転を伝達する構造部材に、少なくとも２つの弾性部材を内挿し、前記入力軸の回転数の変化に応じて、前記構造部材に作用する弾性部材のばね定数の可変機構が設けられた回転伝達装置を用いることにより、前記の課題を解決したのである。 In order to solve the above-described problems, the present invention inserts at least two elastic members into a structural member that transmits rotation from an input shaft, and in the structural member according to a change in the rotational speed of the input shaft. By using a rotation transmission device provided with a variable mechanism for the spring constant of the elastic member that acts, the above-mentioned problem has been solved.

また、前記構造部材として、前記入力軸の回転が伝達される内包部材、及び前記回転を外部に伝達するためのプーリを構成する外包部材を用い、前記内包部材を少なくとも２つの部材から構成し、前記の内包部材を構成する各部材をそれぞれ、前記外包部材と弾性部材を介して連接し、前記ばね定数の可変機構として、前記入力軸の回転数の変化に応じて、前記内包部材の各部材の少なくとも２つの連結・分離を行う内包部材連結・分離機構を用いてもよい。
この内包部材連結・分離機構としては、スプラグ式ワンウェイクラッチ、遠心式摩擦クラッチ、遠心式かみ合いクラッチ等の遠心力により前記内包部材の各部材の少なくとも２つの連結・分離が行われる機構をもちいることができる。 Further, as the structural member, an internal member that transmits the rotation of the input shaft, and an external member that constitutes a pulley for transmitting the rotation to the outside, the internal member is composed of at least two members, Each member constituting the inner member is connected to the outer member via an elastic member, and each member of the inner member is used as a variable mechanism of the spring constant according to a change in the rotational speed of the input shaft. An internal member connection / separation mechanism that performs at least two connection / separation of the above may be used.
As the internal member connection / separation mechanism, a mechanism in which at least two members of the internal member are connected / separated by a centrifugal force such as a sprag type one-way clutch, a centrifugal friction clutch, a centrifugal meshing clutch, or the like is used. Can do.

この発明は、構造部材内に少なくとも２つの弾性部材を用いるので、この構造部材の状態によっては、複数の弾性部材が共同して作用し、各弾性部材が別々に作用する場合に比べて、ばね定数を変化させることができる。このばね定数の変化により、駆動装置の回転数の高低の変化に対応して、生じる回転脈動を減衰させることが可能となる。
特に、構造部材として、入力軸の回転が伝達される内包部材と前記回転を外部に伝達するためのプーリを構成する外包部材からなり、この内包部材が少なくとも２つの部材から構成されている場合、各弾性部材を、内包部材の各部材と外包部材との間に配することにより、内包部材の各部材と外包部材とが弾性部材を介して連接することができる。また、内包部材連結・分離機構を用いることによって、内包部材の複数の部材が連結したり、離脱させることが可能となる。このため、内包部材の複数の部材同士が連結すると、その各部材に配されている弾性部材は、構造部材全体として見ると１つの弾性部材として働くこととなり、ばね定数が変化することとなる。これにより、駆動装置の回転数の高低の変化に対応して、生じる回転脈動を減衰させることが可能となる。 Since this invention uses at least two elastic members in the structural member, depending on the state of the structural member, a plurality of elastic members act together, and each elastic member acts separately compared to the case where the spring acts separately. The constant can be changed. Due to the change in the spring constant, it is possible to attenuate the generated rotational pulsation in response to the change in the rotational speed of the driving device.
In particular, the structural member includes an inner member that transmits the rotation of the input shaft and an outer member that forms a pulley for transmitting the rotation to the outside, and the inner member is composed of at least two members. By disposing each elastic member between each member of the inner packaging member and the outer packaging member, each member of the inner packaging member and the outer packaging member can be connected via the elastic member. Further, by using the inclusion member connecting / separating mechanism, a plurality of members of the inclusion member can be connected or detached. For this reason, when a plurality of members of the encapsulating member are connected to each other, the elastic member arranged in each member acts as one elastic member when viewed as the whole structural member, and the spring constant changes. As a result, it is possible to attenuate the generated rotational pulsation in response to a change in the rotational speed of the driving device.

この発明の回転伝達装置の実施形態を示す断面図Sectional drawing which shows embodiment of the rotation transmission apparatus of this invention 図１（ａ）のｂ−ｂ断面図Bb sectional view of Drawing 1 (a) 図１（ａ）のｃ−ｃ断面図Cc cross-sectional view of FIG. （ｄ−１）（ｄ−２）図１（ｃ）に示すスプラグ式ワンウェイクラッチの動きを示す部分拡大断面図(D-1) (d-2) Partial enlarged sectional view showing the movement of the sprag type one-way clutch shown in FIG. 図１（ｂ）のｅ−ｅ断面図Ee sectional view of FIG. （ａ）（ｂ）図１（ａ）〜（ｅ）に示す回転伝達装置のばね定数の可変機構の機作を示す作用図(A) (b) Operational diagram showing the mechanism of the variable mechanism of the spring constant of the rotation transmission device shown in FIGS. この発明の回転伝達装置の外包部材であるプーリとして、スプロケットを用いた場合の例を示す断面図Sectional drawing which shows the example at the time of using a sprocket as a pulley which is an outer packet member of the rotation transmission apparatus of this invention （ａ）回転数とばね荷重との関係を示すグラフ、（ｂ）回転数と第１弾性部材、又は第１弾性部材＋第２弾性部材のばね荷重との関係を示すグラフ(A) Graph showing the relationship between the rotational speed and the spring load, (b) Graph showing the relationship between the rotational speed and the spring load of the first elastic member, or the first elastic member + the second elastic member. （ａ）（ｂ）遠心式摩擦クラッチの動きを示す部分拡大断面図(A) (b) Partial expanded sectional view which shows the motion of a centrifugal friction clutch （ａ）（ｂ）遠心式かみ合いクラッチの動きを示す部分拡大断面図(A) (b) Partial expanded sectional view which shows the motion of a centrifugal meshing clutch

以下、図面に基づき、本発明の第１の実施形態について説明する。
この発明にかかる回転伝達装置は、入力軸２３からの回転を補機等の外部に伝達する構造部材に、少なくとも２つの弾性部材を内挿し、前記入力軸２３の回転数の変化に応じて、前記構造部材に作用する弾性部材のばね定数の可変機構が設けられた装置である。 Hereinafter, a first embodiment of the present invention will be described with reference to the drawings.
In the rotation transmission device according to the present invention, at least two elastic members are inserted into a structural member that transmits the rotation from the input shaft 23 to the outside such as an auxiliary machine, and in accordance with the change in the rotation speed of the input shaft 23, It is an apparatus provided with a mechanism for changing a spring constant of an elastic member acting on the structural member.

この回転伝達装置１１の具体例として、図１（ａ）〜（ｅ）に示す装置をあげることができる。
この回転伝達装置１１においては、入力軸２３からの回転を伝達する構造部材として、内周面側に前記入力軸２３が挿通され、直接、回転が伝達される内包部材１２、及び前記回転を外部に伝達するためのプーリを構成する外包部材１３からなる。そして、この内包部材１２は、少なくとも２つの部材から構成される。
この内包部材は、図１（ａ）〜（ｅ）の回転伝達装置１１においては、２つの部材から構成されており、入力軸２３と連接する位置に第１内包部材１２ａが配され、また、外包部材１３と主に接する位置に第２内包部材１２ｂが配される。 Specific examples of the rotation transmission device 11 include the devices shown in FIGS.
In this rotation transmission device 11, as a structural member for transmitting rotation from the input shaft 23, the input shaft 23 is inserted on the inner peripheral surface side, and the rotation is transmitted directly to the inner member 12 that transmits rotation. It consists of the outer packaging member 13 which comprises the pulley for transmitting to. The inner member 12 is composed of at least two members.
In the rotation transmission device 11 of FIGS. 1 (a) to 1 (e), this inner member is composed of two members, and the first inner member 12a is arranged at a position connected to the input shaft 23. The second inner member 12b is disposed at a position mainly contacting the outer member 13.

図１（ａ）（ｂ）（ｃ）（ｅ）に示すように、前記の第１内包部材１２ａと第２内包部材１２ｂとは、第２内包部材１２ｂの内周面が第１内包部材１２ａの外周面の一部と対向するように配される。さらに、第２内包部材１２ｂと外包部材１３とは、第２内包部材１２ｂの外周面が外包部材１３の内周面の一部と対向するように配される。 As shown in FIGS. 1A, 1B, 1C, and 1E, the first inner member 12a and the second inner member 12b are such that the inner peripheral surface of the second inner member 12b is the first inner member 12a. It arrange | positions so that a part of outer peripheral surface may be opposed. Further, the second inner packaging member 12 b and the outer packaging member 13 are arranged such that the outer circumferential surface of the second inner packaging member 12 b faces a part of the inner circumferential surface of the outer packaging member 13.

また、外包部材１３の内周面のうち、第２内包部材１２ｂと対向しない面の一部に、複数の凸部が形成され、かつ、この凸部の一部に凹部が形成された凹凸部１６を有する。さらに、第１内包部材１２ａの外周面のうち、第２内包部材１２ｂの内周面と対向しない面の一部に第１凸部１７が形成される。そして、前記凹凸部１６には、前記第１凸部１７と第１弾性部材１４ａが配される。これにより、外包部材１３と第１内包部材１２ａとは、第１弾性部材１４ａを介して円周方向に連接される。 In addition, an uneven portion in which a plurality of convex portions are formed on a part of the inner peripheral surface of the outer packet member 13 that does not face the second inner member 12b, and a concave portion is formed on a part of the convex portion. 16 Furthermore, the 1st convex part 17 is formed in a part of surface which does not oppose the inner peripheral surface of the 2nd inner packaging member 12b among the outer peripheral surfaces of the 1st inner packaging member 12a. In addition, the first convex portion 17 and the first elastic member 14a are disposed on the concave and convex portion 16. Thereby, the outer packet member 13 and the first inner member 12a are connected in the circumferential direction via the first elastic member 14a.

さらに、外包部材１３の内径面の一部に設けられる凹凸部１６と隣の凹凸部１６との間には空間部１８が設けられ、この空間部１８に、第２内包部材１２ｂの軸方向に形成される第２凸部１９と第２弾性部材１４ｂが配される。これにより、外包部材１３と第２内包部材１２ｂとは、第２弾性部材１４ｂを介して円周方向に連接される。 Furthermore, a space portion 18 is provided between the uneven portion 16 provided on a part of the inner diameter surface of the outer packet member 13 and the adjacent uneven portion 16, and the space portion 18 is provided in the axial direction of the second inner member 12 b. The 2nd convex part 19 and the 2nd elastic member 14b which are formed are arranged. Thereby, the outer packet member 13 and the second inner member 12b are connected in the circumferential direction via the second elastic member 14b.

前記第１弾性部材１４ａや第２弾性部材１４ｂは、弾性を有するものであれば用いることができ、その具体例としては、円弧状のコイルばね等をあげることができる。 The first elastic member 14a and the second elastic member 14b can be used as long as they have elasticity, and specific examples thereof include an arc-shaped coil spring.

前記ばね定数の可変機構としては、内包部材１２の各部材の少なくとも２つの連結・分離を行う内包部材連結・分離機構があげられる。この内包部材連結・分離機構として、遠心力により前記内包部材の各部材の少なくとも２つの連結・分離が行われる機構を用いると、前記入力軸２３の回転数の変化に応じて、各内包部材を連結させたり、分離させたりすることが可能となり、好ましい。 Examples of the variable mechanism of the spring constant include an internal member connecting / separating mechanism that connects and separates at least two members of the internal member 12. When a mechanism in which at least two members of the inner member are connected / separated by centrifugal force is used as the inner member connecting / separating mechanism, each inner member is changed according to a change in the rotational speed of the input shaft 23. It can be connected or separated, which is preferable.

このような遠心力による内包部材連結・分離機構の具体例としては、図１（ｃ）に示すような、第１内包部材１２ａの外周面と第２内包部材１２ｂの内周面とが対向する部分に設けられる、スプラグ１５ａとばね等の弾性部材１５ｂとから構成されるスプラグ式ワンウェイクラッチ１５があげられる。 As a specific example of such an internal member connection / separation mechanism by centrifugal force, the outer peripheral surface of the first internal member 12a and the inner peripheral surface of the second internal member 12b are opposed to each other as shown in FIG. An example is a sprag type one-way clutch 15 that is provided at a portion and includes a sprag 15a and an elastic member 15b such as a spring.

次に、このスプラグ式ワンウェイクラッチ１５の機作について説明する。
入力軸２３が回転すると、その回転は、まず、入力軸２３と連結される第１内包部材１２ａに伝達される。
入力軸２３から伝達される回転数が小さいとき（低回転のとき）は、図１（ｄ）の（ｄ−１）に示すように、スプラグ式ワンウェイクラッチ１５を構成するスプラグ１５ａは、弾性部材１５ｂに押された状態を保持し、第１内包部材１２ａと第２内包部材１２ｂは分離した状態のままとなる。このため、図２（ａ）に示すように、第１内包部材１２ａの回転は、第１弾性部材１４ａを介して外包部材１３に伝達される。一方、第１内包部材１２ａと第２内包部材１２ｂとは連結されていないので、第１内包部材１２ａの回転は、第２内包部材１２ｂに伝達されない。このため、入力軸２３から伝達される回転は、第１内包部材１２ａ、第１弾性部材１４ａを介して外包部材１３に伝達される。
このとき、エンジン等の駆動装置で回転と共に生じる脈動は、入力軸２３から第１内包部材１２ａ、第１弾性部材１４ａに伝達されるが、この第１弾性部材１４ａとして、適切なばね定数を有する弾性部材を用いることにより、脈動を減衰させることができる。 Next, the operation of the sprag type one-way clutch 15 will be described.
When the input shaft 23 rotates, the rotation is first transmitted to the first inner member 12 a connected to the input shaft 23.
When the rotation speed transmitted from the input shaft 23 is small (when the rotation speed is low), as shown in (d-1) of FIG. 1 (d), the sprag 15a constituting the sprag type one-way clutch 15 is an elastic member. The state pushed by 15b is hold | maintained, and the 1st inclusion member 12a and the 2nd inclusion member 12b remain in the state isolate | separated. For this reason, as shown to Fig.2 (a), rotation of the 1st inclusion member 12a is transmitted to the enclosure member 13 via the 1st elastic member 14a. On the other hand, since the 1st inclusion member 12a and the 2nd inclusion member 12b are not connected, rotation of the 1st inclusion member 12a is not transmitted to the 2nd inclusion member 12b. For this reason, the rotation transmitted from the input shaft 23 is transmitted to the outer packet member 13 via the first inner member 12a and the first elastic member 14a.
At this time, the pulsation generated along with the rotation of the driving device such as the engine is transmitted from the input shaft 23 to the first inner member 12a and the first elastic member 14a. The first elastic member 14a has an appropriate spring constant. By using an elastic member, pulsation can be attenuated.

次に、入力軸２３から伝達される回転数が大きくなったとき（高回転のとき）、遠心力が大きくなり、図１（ｄ）の（ｄ−２）に示すように、スプラグ１５ａが弾性部材１５ｂの付勢力に抗して動き、第１内包部材１２ａと第２内包部材１２ｂとの間で噛み込みが生じる。このため、第１内包部材１２ａと第２内包部材１２ｂとは、スプラグ１５ａを介して連結される。このとき、図２（ｂ）に示すように、入力軸２３から伝達される回転は、第１内包部材１２ａと共に第２内包部材１２ｂに伝達される。第１内包部材１２ａに伝達された回転は、第１弾性部材１４ａを介して外包部材１３に伝達され、また、第２内包部材１２ｂに伝達された回転は、第２弾性部材１４ｂを介して外包部材１３に伝達される。
このとき、エンジン等の駆動装置で回転と共に生じる脈動は、入力軸２３から第１内包部材１２ａ、第１弾性部材１４ａに伝達されると共に、入力軸２３から第１内包部材１２ａ、第２内包部材１２ｂ、第２弾性部材１４ｂに伝達される。すなわち、第１弾性部材１４ａと第２弾性部材１４ｂの両方に回転と共に脈動が伝達される。このとき、第１弾性部材１４ａと第２弾性部材１２ｂとは同時に動くので、２つの弾性部材は１つの弾性部材として働くこととなり、全体としてばね定数は変化することとなる。このため、第２弾性部材１４ｂとして、適切なばね定数を有する弾性部材を用いることにより、第１弾性部材１４ａと第２弾性部材１４ｂとを組み合わせたときのばね定数を適切な値とすることができ、高回転における脈動を減衰させることができる。 Next, when the number of rotations transmitted from the input shaft 23 increases (when the rotation speed is high), the centrifugal force increases, and the sprag 15a is elastic as shown in FIG. 1 (d) (d-2). It moves against the urging force of the member 15b, and biting occurs between the first inclusion member 12a and the second inclusion member 12b. For this reason, the 1st inclusion member 12a and the 2nd inclusion member 12b are connected via the sprag 15a. At this time, as shown in FIG. 2B, the rotation transmitted from the input shaft 23 is transmitted to the second inner member 12b together with the first inner member 12a. The rotation transmitted to the first inner member 12a is transmitted to the outer member 13 via the first elastic member 14a, and the rotation transmitted to the second inner member 12b is included in the outer packet via the second elastic member 14b. It is transmitted to the member 13.
At this time, the pulsation generated by the rotation of the driving device such as the engine is transmitted from the input shaft 23 to the first inclusion member 12a and the first elastic member 14a, and from the input shaft 23 to the first inclusion member 12a and the second inclusion member. 12b and the second elastic member 14b. That is, pulsation is transmitted to both the first elastic member 14a and the second elastic member 14b together with the rotation. At this time, since the first elastic member 14a and the second elastic member 12b move simultaneously, the two elastic members act as one elastic member, and the spring constant as a whole changes. For this reason, by using an elastic member having an appropriate spring constant as the second elastic member 14b, the spring constant when the first elastic member 14a and the second elastic member 14b are combined can be set to an appropriate value. The pulsation at high rotation can be attenuated.

回転数が増加していくと、第１弾性部材１４ａのみが働いている状態から、第１弾性部材１４ａと第２弾性部材１４ｂの両方が働いている状態に移行することは、図４（ａ）に示すグラフからも明らかである。すなわち、図４（ａ）のグラフに示すように、回転数が上昇していくにしたがって、ばね荷重が直線的に増加し、途中で折れ曲がり、増加度がさらに上がる。ところで、図４（ｂ）のグラフに示すように、内包部材１２と外包部材１３との位相差が大きくなると、第１弾性部材１４ａのみが働いているときより、第１弾性部材１４ａと第２弾性部材１４ｂの両方が働いているときの方が、ばね荷重が大きくなることから、図４（ａ）のグラフにおいては、途中で折れ曲がった箇所で、スプラグ１５ａが第１内包部材１２ａと第２内包部材１２ｂとの間で噛み込み、第１内包部材１２ａの第１弾性部材１４ａのみならず、第２内包部材１２ｂの第２弾性部材１４ｂも同時に働き始めたといえるのである。 As the number of rotations increases, the state where only the first elastic member 14a is working shifts to the state where both the first elastic member 14a and the second elastic member 14b are working. It is also clear from the graph shown in FIG. That is, as shown in the graph of FIG. 4A, as the rotational speed increases, the spring load increases linearly, bends in the middle, and the degree of increase further increases. By the way, as shown in the graph of FIG. 4B, when the phase difference between the inner packet member 12 and the outer packet member 13 is increased, the first elastic member 14a and the second elastic member 14a are compared with the first elastic member 14a and the second elastic member 14a. Since the spring load becomes larger when both of the elastic members 14b are working, in the graph of FIG. 4 (a), the sprag 15a and the second inclusion member 12a and the second inclusion member 12a are bent in the middle. It can be said that not only the first elastic member 14a of the first inner member 12a but also the second elastic member 14b of the second inner member 12b began to work simultaneously with the inner member 12b.

このような機作により、この発明に係る回転伝達装置は、伝達される回転数の変化に応じて、内挿された弾性部材のばね定数を変化させることができる。このため、エンジン等の駆動装置の回転数の変化によって生じる脈動の変化に対応することができ、低回転時であっても、高回転時であっても、生じる脈動を有効に減衰させることが可能となる。 With such a mechanism, the rotation transmission device according to the present invention can change the spring constant of the inserted elastic member in accordance with the change in the transmitted rotation speed. For this reason, it is possible to cope with a change in pulsation caused by a change in the number of revolutions of a drive device such as an engine, and effectively attenuate the generated pulsation even at a low speed or at a high speed. It becomes possible.

この遠心力による内包部材連結・分離機構の他の例としては、図５（ａ）（ｂ）に示す遠心式摩擦クラッチ２１や、図６（ａ）（ｂ）に示す遠心式かみ合いクラッチ２２等をあげることができる。
前記遠心式摩擦クラッチ２１は、第１内包部材１２ａに取り付けられており、シュー２１ａと弾性部材２１ｂとから構成される。
この遠心式摩擦クラッチ２１の機作は、スプラグ１５ａとシュー２１ａとが異なる以外は、スプラグ式ワンウェイクラッチ１５の機作と同様である。すなわち、低回転のときは、図５（ａ）に示すように、シュー２１ａが弾性部材２１ｂに押された状態に保持され、第１内包部材１２ａと第２内包部材１２ｂは分離した状態のままとなる。一方、高回転のときは、遠心力が大きくなり、図５（ｂ）に示すように、シュー２１ａが弾性部材２１ｂの付勢力に抗して動き、第２内包部材１２ｂと接触が生じる。このシュー２１ａの第２内包部材１２ｂとの接触部分は摩擦係数が高いため、シュー２１ａが第２内包部材１２ｂと共に回転することとなる。このため、第１内包部材１２ａと第２内包部材１２ｂとは、シュー２１ａを介して連結される。このシュー２１ａの動きにより、前記したスプラグ式ワンウェイクラッチ１５の機作と同様の機作が生じる。 Other examples of the enclosing member connecting / separating mechanism using the centrifugal force include the centrifugal friction clutch 21 shown in FIGS. 5 (a) and 5 (b), the centrifugal meshing clutch 22 shown in FIGS. 6 (a) and 6 (b), and the like. Can give.
The centrifugal friction clutch 21 is attached to the first inner member 12a, and includes a shoe 21a and an elastic member 21b.
The operation of the centrifugal friction clutch 21 is the same as that of the sprag type one-way clutch 15 except that the sprag 15a and the shoe 21a are different. That is, at the time of low rotation, as shown in FIG. 5A, the shoe 21a is held in a state of being pushed by the elastic member 21b, and the first inclusion member 12a and the second inclusion member 12b remain separated. It becomes. On the other hand, at the time of high rotation, the centrifugal force increases, and as shown in FIG. 5B, the shoe 21a moves against the urging force of the elastic member 21b, and contact with the second inclusion member 12b occurs. The contact portion of the shoe 21a with the second inner member 12b has a high friction coefficient, so the shoe 21a rotates together with the second inner member 12b. For this reason, the 1st inclusion member 12a and the 2nd inclusion member 12b are connected via shoe 21a. Due to the movement of the shoe 21a, the same operation as that of the sprag type one-way clutch 15 described above occurs.

次に、前記遠心式かみ合いクラッチ２２は、第１内包部材１２ａに取り付けられており、先端部に突起状の係合子２２ｃを有するラチェット爪２２ａと、弾性部材２２ｂとから構成される。また、この遠心式かみ合いクラッチ２２が配される第１内包部材１２ａの外径面と対向する第２内包部材１２ｂの内径面には、前記係合子２２ｃとかみ合う歯２２ｄが設けられる。
この遠心式かみ合いクラッチ２２の機作は、スプラグ１５ａとラチェット爪２２ａとが異なる点、及び第２内包部材１２ｂの内径面にラチェット爪２２ａの係合子２２ｃとかみ合う歯２２ｄが設けられる点以外は、スプラグ式ワンウェイクラッチ１５の機作と同様である。すなわち、低回転のときは、図６（ａ）に示すように、ラチェット爪２２ａが弾性部材２２ｂに押された状態に保持され、第１内包部材１２ａと第２内包部材１２ｂは分離した状態のままとなる。一方、高回転のときは、遠心力が大きくなり、図６（ｂ）に示すように、ラチェット爪２２ａが弾性部材２２ｂの付勢力に抗して動き、係合子２２ｃが第２内包部材１２ｂに向かって突き出る状態となる。そして、第２内包部材１２ｂの歯２２ｄとかみ合う。このため、ラチェット爪２２ａが第２内包部材１２ｂと共に回転することとなる。このため、第１内包部材１２ａと第２内包部材１２ｂとは、ラチェット爪２２ａを介して連結される。このラチェット爪２２ａの動きにより、前記したスプラグ式ワンウェイクラッチ１５の機作と同様の機作が生じる。 Next, the centrifugal meshing clutch 22 is attached to the first inclusion member 12a, and is composed of a ratchet pawl 22a having a projecting engagement element 22c at the tip and an elastic member 22b. Further, teeth 22d that engage with the engaging elements 22c are provided on the inner diameter surface of the second inner member 12b opposite to the outer diameter surface of the first inner member 12a on which the centrifugal meshing clutch 22 is disposed.
The operation of the centrifugal meshing clutch 22 is different from that of the sprag 15a and the ratchet pawl 22a, except that the inner diameter surface of the second inner member 12b is provided with teeth 22d that engage with the engagement elements 22c of the ratchet pawl 22a. The operation is the same as that of the sprag type one-way clutch 15. That is, at the time of low rotation, as shown in FIG. 6A, the ratchet pawl 22a is held in a state of being pushed by the elastic member 22b, and the first inner member 12a and the second inner member 12b are separated from each other. Will remain. On the other hand, when the rotation speed is high, the centrifugal force increases, and as shown in FIG. 6B, the ratchet pawl 22a moves against the urging force of the elastic member 22b, and the engaging member 22c moves to the second inner member 12b. It will be in a state of protruding toward. And it meshes with the teeth 22d of the second enclosing member 12b. For this reason, the ratchet pawl 22a rotates together with the second inclusion member 12b. For this reason, the 1st inclusion member 12a and the 2nd inclusion member 12b are connected via ratchet nail | claw 22a. Due to the movement of the ratchet pawl 22a, the same mechanism as that of the sprag type one-way clutch 15 is generated.

ところで、前記外包部材１３であるプーリとしては、入力軸２３から伝達される回転を補機に伝える機能を有していればよく、Ｖリブプーリや、図３に示すようなスプロケット形状を有するプーリ等、種々のプーリを用いることができる。このスプロケット形状を有するプーリを用いる場合は、この発明に係る回転伝達装置をタイミングチェーン等のシステム等に採用することが可能となる。 By the way, the pulley that is the outer cover member 13 only needs to have a function of transmitting the rotation transmitted from the input shaft 23 to the auxiliary machine, such as a V-rib pulley, a pulley having a sprocket shape as shown in FIG. Various pulleys can be used. When the pulley having the sprocket shape is used, the rotation transmission device according to the present invention can be employed in a system such as a timing chain.

この発明にかかる回転伝達装置は、エンジン等の駆動装置から回転とともに出力された脈動を減衰することができ、回転のみを補機に伝えることが可能となる。 The rotation transmission device according to the present invention can attenuate the pulsation output together with the rotation from a driving device such as an engine, and can transmit only the rotation to the auxiliary machine.

１１回転伝達装置
１２内包部材
１２ａ第１内包部材
１２ｂ第２内包部材
１３外包部材
１４ａ第１弾性部材
１４ｂ第２弾性部材
１５スプラグ式ワンウェイクラッチ
１５ａスプラグ
１５ｂ弾性部材
１６凹凸部
１７第１凸部
１８空間部
１９第２凸部
２１遠心式摩擦クラッチ
２１ａシュー
２１ｂ弾性部材
２２遠心式かみ合いクラッチ
２２ａラチェット爪
２２ｂ弾性部材
２２ｃ係合子
２２ｄ歯
２３入力軸 11 rotation transmission device 12 inner member 12a first inner member 12b second inner member 13 outer member 14a first elastic member 14b second elastic member 15 sprag type one-way clutch 15a sprag 15b elastic member 16 uneven portion 17 first convex portion 18 space Part 19 second convex part 21 centrifugal friction clutch 21a shoe 21b elastic member 22 centrifugal meshing clutch 22a ratchet pawl 22b elastic member 22c engagement element 22d tooth 23 input shaft

Claims

入力軸からの回転を伝達する構造部材に、少なくとも２つの弾性部材を内挿し、
前記入力軸の回転数の変化に応じて、前記構造部材に作用する弾性部材のばね定数の可変機構が設けられた回転伝達装置。 At least two elastic members are inserted into the structural member that transmits the rotation from the input shaft,
A rotation transmission device provided with a mechanism for changing a spring constant of an elastic member acting on the structural member in accordance with a change in the rotational speed of the input shaft.

前記構造部材は、前記入力軸の回転が伝達される内包部材、及び前記回転を外部に伝達するためのプーリを構成する外包部材からなり、
前記内包部材は、少なくとも２つの部材から構成されており、
前記の内包部材を構成する各部材は、それぞれ、前記外包部材と弾性部材を介して連接されており、
前記ばね定数の可変機構は、前記入力軸の回転数の変化に応じて、前記内包部材の各部材の少なくとも２つの連結・分離を行う内包部材連結・分離機構である請求項１に記載の回転伝達装置。 The structural member includes an inner member that transmits the rotation of the input shaft, and an outer member that constitutes a pulley for transmitting the rotation to the outside.
The inclusion member is composed of at least two members,
Each member constituting the inner packet member is connected to the outer packet member via an elastic member,
2. The rotation according to claim 1, wherein the variable mechanism of the spring constant is an internal member connecting / separating mechanism that connects and separates at least two members of the internal member according to a change in the rotational speed of the input shaft. Transmission device.

前記内包部材連結・分離機構は、遠心力により前記内包部材の各部材の少なくとも２つの連結・分離が行われる機構である請求項２に記載の回転伝達装置。 The rotation transmission device according to claim 2, wherein the inner member connecting / separating mechanism is a mechanism in which at least two members of the inner member are connected / separated by centrifugal force.

前記内包部材連結・分離機構は、スプラグ式ワンウェイクラッチである請求項３に記載の回転伝達装置。 The rotation transmission device according to claim 3, wherein the inclusion member connecting / separating mechanism is a sprag type one-way clutch.

前記内包部材連結・分離機構は、遠心式摩擦クラッチである請求項３に記載の回転伝達装置。 The rotation transmission device according to claim 3, wherein the inner member connecting / separating mechanism is a centrifugal friction clutch.

前記内包部材連結・分離機構は、遠心式かみ合いクラッチである請求項３に記載の回転伝達装置。 The rotation transmission device according to claim 3, wherein the inner member connecting / separating mechanism is a centrifugal meshing clutch.

前記弾性部材が円弧状のコイルばねである請求項１乃至６のいずれか一項に記載の回転伝達装置。 The rotation transmission device according to any one of claims 1 to 6, wherein the elastic member is an arc-shaped coil spring.

前記プーリは、Ｖリブプーリである請求項２乃至７のいずれか一項に記載の回転伝達装置。 The rotation transmission device according to any one of claims 2 to 7, wherein the pulley is a V-rib pulley.

前記プーリは、スプロケット形状を有する請求項２乃至７のいずれか一項に記載の回転伝達装置。 The rotation transmission device according to any one of claims 2 to 7, wherein the pulley has a sprocket shape.