JP6717885B2 - clutch - Google Patents
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- JP6717885B2 JP6717885B2 JP2018129090A JP2018129090A JP6717885B2 JP 6717885 B2 JP6717885 B2 JP 6717885B2 JP 2018129090 A JP2018129090 A JP 2018129090A JP 2018129090 A JP2018129090 A JP 2018129090A JP 6717885 B2 JP6717885 B2 JP 6717885B2
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Description
本発明は、入力軸と出力軸との間の動力伝達状態を変更するクラッチ装置、特に、入力軸からの正・逆回転の動力は出力軸に伝達するが、入力軸と同じ方向にこれに対して回転しようとする出力軸の回転は空転して入力軸に伝達しないクラッチに関するものである。 The present invention relates to a clutch device for changing the power transmission state between an input shaft and an output shaft, and in particular, forward/reverse rotation power from the input shaft is transmitted to the output shaft, but in the same direction as the input shaft. The rotation of the output shaft, which is about to rotate, is related to the clutch that idles and is not transmitted to the input shaft.
モーターなどの駆動源から機械装置あるいは作業機器等を駆動する動力伝達系では、駆動する機器の特性に対応するよう各種の伝達装置が使用される。このような伝達装置の一つにワンウェイクラッチがある。ワンウェイクラッチは広く知られた伝達装置であり、これには、正逆いずれか一方の回転のみを伝達し、いずれか他方の回転は空転して遮断される形式（空転式）のものがある。 2. Description of the Related Art In a power transmission system that drives a mechanical device or a work device from a drive source such as a motor, various transmission devices are used so as to correspond to the characteristics of the driven device. One of such transmission devices is a one-way clutch. The one-way clutch is a widely known transmission device, and there is a type in which only one of the forward and reverse rotations is transmitted and the other rotation is idled and interrupted (idle type).
空転式のワンウェイクラッチは、例えば、自動車の電動スライドドアや自動開閉便座において駆動源のモーターを保護する目的で使用される。即ち、従動部材であるスライドドアや便座がモーターによって開閉動している最中に、この開閉動と同じ方向に従動部材が外力によって強制的に作動させられた場合には、この従動部材の作動によってモーターが強制的に回転され、損傷してしまう場合がある。これを防止するために、モーターと従動部材との間に空転式のワンウェイクラッチを設け、モーターからの回転は従動部材に伝達するが、従動部材に加えられたモーターの回転と同じ方向の回転はこれをモーターに対して空転させて伝達しないようにする。 The idle type one-way clutch is used for the purpose of protecting a motor of a drive source in, for example, an electric sliding door of an automobile or an automatic opening/closing toilet seat. That is, when the driven member is forced to be actuated by an external force while the sliding door or the toilet seat, which is the driven member, is being opened and closed by the motor, the actuation of the driven member is performed. May force the motor to rotate and damage it. In order to prevent this, a idle type one-way clutch is provided between the motor and the driven member, and rotation from the motor is transmitted to the driven member, but rotation in the same direction as rotation of the motor applied to the driven member is prevented. This should be idled to the motor so that it will not be transmitted.
空転式のワンウェイクラッチとしては、例えば、本出願人の創案に係る特許第３５０１３５２号に記載されたワンウェイクラッチが知られており、これについて、図１０を参照して説明する。
図１０に示すとおり、このワンウェイクラッチでは、シャフトのような内側部材Ｉ（入力軸）と外輪のような外側部材Ｏ（出力軸）とが楔形のポケットＰを複数形成しており、そのポケットＰにはローラーＲが配置されている。内側部材Ｉが外側部材Ｏに対して同図において時計方向に回転するときは、ローラーＲはポケットＰ内を楔の広い方向に移動して内側部材Ｉと外側部材Ｏとの間で噛み込むことはなく、内側部材Ｉと外側部材Ｏは互いに回転することができる（相対回転可能な状態）。つまり、内側部材Ｉと外側部材Ｏは空転する。しかし、内側部材Ｉが外側部材Ｏに対して同図において反時計方向に回転、つまり逆回転するときは、ローラーＲはポケットＰ内を楔の狭い方向に移動して内側部材Ｉと外側部材Ｏとの間で噛み込みを生じ、内側部材Ｉと外側部材Ｏは互いに回転することができない（相対回転不能な状態）。
As the idling one-way clutch, for example, the one-way clutch described in Japanese Patent No. 3501352 of the present applicant is known, which will be described with reference to FIG.
As shown in FIG. 10, in this one-way clutch, an inner member I (input shaft) such as a shaft and an outer member O (output shaft) such as an outer ring form a plurality of wedge-shaped pockets P. A roller R is arranged in the. When the inner member I rotates clockwise with respect to the outer member O in the figure, the roller R moves in the wide direction of the wedge in the pocket P to be caught between the inner member I and the outer member O. However, the inner member I and the outer member O can rotate relative to each other (relatively rotatable state). That is, the inner member I and the outer member O run idle. However, when the inner member I rotates counterclockwise with respect to the outer member O in the figure, that is, in the reverse direction, the roller R moves in the narrow direction of the wedge in the pocket P to move the inner member I and the outer member O. The inner member I and the outer member O cannot rotate relative to each other (a state in which they cannot rotate relative to each other).
ワンウェイクラッチは、上述したとおり、正逆いずれか一方の回転のみを伝達し、いずれか他方の回転は遮断するものである。そのため、これを正逆両方向に回転するモーターの保護を目的に使用する場合には、相互に反対方向の回転を伝達可能とする２つのワンウェイクラッチを設け、従動部材の正回転時と逆回転時とで２つのワンウェイクラッチを電子制御によって切り替えて使用する必要があり、装置が複雑なものとなる。 As described above, the one-way clutch transmits only one of the normal and reverse rotations and interrupts the other rotation. Therefore, when this is used for the purpose of protecting the motor that rotates in both forward and reverse directions, two one-way clutches that can transmit rotations in opposite directions are provided, and when the driven member rotates forward and backward. Since it is necessary to switch between the two one-way clutches by using the electronic control, the device becomes complicated.
上記の課題を解決するため、本発明のクラッチは、出力軸に連結された２つの遊星歯車機構を軸方向に重ねて配置し、夫々の遊星歯車機構の太陽歯車は相互に反対方向に空転するよう設定された一方向クラッチを介して出力軸に連結され、入力軸が回転したときは、その回転方向に応じて、一方の遊星歯車機構が出力軸と一体となって回転すると共に他方の遊星歯車機構は空転し、出力軸が入力軸からの回転と同じ方向に回転したときは、一方の遊星歯車機構の太陽歯車にのみ出力軸の回転が伝達されるが、この太陽歯車と噛み合う遊星歯車が空転することで、入力軸への回転の伝達が遮断されるようにしたものである。すなわち、本発明は、
「共通の中心軸の周りで回転可能な入力軸及び出力軸と、前記出力軸に連結された２つの遊星歯車機構とを備え、
前記２つの遊星歯車機構は夫々軸方向に重ねて配置され、前記出力軸に一方向クラッチを介して連結された太陽歯車、及び前記太陽歯車と噛み合う遊星歯車を備え、前記２つの遊星歯車機構の太陽歯車に配設された一方向クラッチの各々は前記出力軸に対して相互に反対の回転方向で空転するよう設定され、前記２つの遊星歯車機構の遊星歯車は夫々前記共通の中心軸の周りを回転可能な共通のキャリアによって回転可能に軸支されており、
前記入力軸には押圧片が固着されると共に前記キャリアには前記押圧片が嵌り込む凹部が形成され、前記２つの遊星歯車機構の遊星歯車は前記凹部の周方向両側に相互に配置され、前記押圧片には前記遊星歯車の自転を規制する規制手段が固着されており、
前記入力軸が回転したときは、その回転方向に応じて、前記規制手段が前記２つの遊星歯車機構のいずれか一方の遊星歯車の自転を規制すると共に、前記押圧片が前記凹部で前記キャリアと当接してこれを周方向に押し、前記２つの遊星歯車機構が前記出力軸と一体となって回転し、
前記出力軸が前記入力軸からの回転と同じ方向に回転したときは、前記２つの遊星歯車機構の太陽歯車のうち、自転が規制されていない遊星歯車と噛み合う太陽歯車に前記出力軸の回転が伝達されるが、前記出力軸の回転が伝達された前記太陽歯車と噛み合う前記遊星歯車は空転し、前記出力軸から前記入力軸への回転の伝達は遮断される」
ことを特徴とするクラッチとなっている。
In order to solve the above-mentioned problems, the clutch of the present invention has two planetary gear mechanisms connected to an output shaft, which are axially overlapped with each other, and the sun gears of the respective planetary gear mechanisms idle in mutually opposite directions. When the input shaft rotates via the one-way clutch set as described above, one planetary gear mechanism rotates integrally with the output shaft and the other planetary gear rotates depending on the rotation direction. The gear mechanism idles, and when the output shaft rotates in the same direction as the rotation from the input shaft, the rotation of the output shaft is transmitted only to the sun gear of one planetary gear mechanism. When the wheel rotates idly, the transmission of rotation to the input shaft is cut off. That is, the present invention is
"It comprises an input shaft and an output shaft rotatable about a common central axis, and two planetary gear mechanisms connected to the output shaft,
The two planetary gear mechanisms are arranged in the axial direction so as to be overlapped with each other, and include a sun gear connected to the output shaft via a one-way clutch, and a planetary gear that meshes with the sun gear. Each of the one-way clutches arranged on the sun gear is set so as to idle in mutually opposite rotational directions with respect to the output shaft, and the planetary gears of the two planetary gear mechanisms respectively rotate around the common central axis. Is rotatably supported by a common carrier that can rotate
A pressing piece is fixed to the input shaft and a recess into which the pressing piece is fitted is formed in the carrier, and the planet gears of the two planetary gear mechanisms are arranged on both sides in the circumferential direction of the recess, and A restraint means for restraining rotation of the planetary gear is fixed to the pressing piece,
When the input shaft rotates, the restricting means restricts the rotation of one of the planetary gears of the two planetary gear mechanisms in accordance with the rotation direction of the input shaft, and the pressing piece serves as the carrier in the recess. Abutting and pushing it in the circumferential direction, the two planetary gear mechanisms rotate integrally with the output shaft,
When the output shaft rotates in the same direction as the rotation from the input shaft, the rotation of the output shaft occurs in the sun gear of the two planetary gear mechanisms that meshes with the planet gear whose rotation is not restricted. It is transmitted, but the planetary gear that meshes with the sun gear to which the rotation of the output shaft has been transmitted idles, and the transmission of rotation from the output shaft to the input shaft is cut off."
It is a clutch that is characterized.
本発明においては、以下のような実施形態であるのが好ましい。すなわち、
前記規制手段の断面は外歯歯車の一部を切り欠いた形状であるのが好ましい。
前記キャリアに形成された前記凹部の側面の形状は前記押圧片の側面の形状と同一であるのが好ましい。
前記キャリアは、板状の基部と、前記基部から軸方向に延びる支持片とを備え、前記支持片は、前記キャリアと一体的に結合されるキャリア補助板によって軸受され、前記基部と前記キャリア補助板とは軸方向に間隔をおいて対向するのが好ましい。
In the present invention, the following embodiments are preferable. That is,
It is preferable that a cross section of the restriction means has a shape in which a part of the external gear is cut out.
The shape of the side surface of the recess formed in the carrier is preferably the same as the shape of the side surface of the pressing piece.
The carrier includes a plate-shaped base and a support piece extending in the axial direction from the base, and the support piece is supported by a carrier auxiliary plate integrally connected to the carrier, and the base and the carrier auxiliary are supported. It is preferable to face the plate at an axial distance.
本発明のクラッチでは、２つの遊星歯車機構が軸方向に重ねて出力軸に連結される。２つの遊星歯車機構は夫々、出力軸に一方向クラッチを介して連結された太陽歯車と、太陽歯車と噛み合う遊星歯車とを備え、２つの遊星歯車機構の遊星歯車は夫々共通のキャリアによって回転可能に軸支される。２つの遊星歯車機構の太陽歯車に配設された一方向クラッチの各々は出力軸に対して相互に反対の回転方向で空転するよう設定される。入力軸には押圧片が固着されると共にキャリアには入力軸に固着された押圧片が嵌り込む凹部が形成され、２つの遊星歯車機構の遊星歯車は凹部の周方向両側に各々配置される。そして、押圧片には遊星歯車の自転を規制する規制手段が固着される。 In the clutch of the present invention, two planetary gear mechanisms are axially overlapped and connected to the output shaft. The two planetary gear mechanisms each include a sun gear that is connected to the output shaft via a one-way clutch, and a planetary gear that meshes with the sun gear. The planetary gears of the two planetary gear mechanisms are rotatable by a common carrier. Is pivotally supported by. Each of the one-way clutches arranged on the sun gears of the two planetary gear mechanisms is set so as to idle in mutually opposite rotational directions with respect to the output shaft. A pressing piece is fixed to the input shaft, a recess is formed in the carrier into which the pressing piece fixed to the input shaft is fitted, and the planetary gears of the two planetary gear mechanisms are arranged on both sides in the circumferential direction of the recess. Then, a restricting means for restricting rotation of the planetary gear is fixed to the pressing piece.
後に図８を参照して詳述するとおり、入力軸が回転すると、その回転方向に応じて、規制手段が２つの遊星歯車機構のいずれか一方の遊星歯車の自転を規制すると共に、押圧片が凹部でキャリアと当接してこれを周方向に押す。これによって、２つの遊星歯車機構のうち、自転が規制された遊星歯車を含む遊星歯車機構は出力軸と一体となって回転し、入力軸から出力軸へ回転が伝達される。このとき、自転が規制されていない遊星歯車を含む遊星歯車機構にあっては、出力軸と一方向クラッチとの間で噛み込みが生じて太陽歯車が回転すると共に、これと噛み合う遊星歯車も回転（つまり空転）する。 As will be described later in detail with reference to FIG. 8, when the input shaft rotates, the restricting means restricts the rotation of one of the planetary gears of the two planetary gear mechanisms in accordance with the rotation direction, and the pressing piece moves. The recess contacts the carrier and pushes it circumferentially. As a result, of the two planetary gear mechanisms, the planetary gear mechanism including the planetary gear whose rotation is restricted rotates together with the output shaft, and the rotation is transmitted from the input shaft to the output shaft. At this time, in a planetary gear mechanism that includes a planetary gear whose rotation is not restricted, the sun gear rotates as a result of biting between the output shaft and the one-way clutch, and the planetary gear that meshes with this also rotates. (That is, idle).
これに対して、出力軸が入力軸からの回転と同じ方向にこれに対して回転すると、
自転が規制された遊星歯車を含む遊星歯車機構にあっては、ローラーは出力軸の外周面との噛み合いが解除される方向へ移動されるため、出力軸の回転が入力軸に伝達されることはない。自転が規制されていない遊星歯車を含む遊星歯車機構にあっては、ローラーは出力軸の外周面との噛み合いが生じる方向へ移動させられるが、太陽歯車と噛み合う遊星歯車は自転が規制されていないため、太陽歯車及び遊星歯車は共に空転する。従って、出力軸の回転が入力軸に伝達されることはない。
On the other hand, if the output shaft rotates in the same direction as the rotation from the input shaft,
In a planetary gear mechanism that includes a planetary gear whose rotation is restricted, the roller is moved in the direction that disengages from the outer peripheral surface of the output shaft, so the rotation of the output shaft is transmitted to the input shaft. There is no. In a planetary gear mechanism that includes a planetary gear whose rotation is not restricted, the roller is moved in the direction that meshes with the outer peripheral surface of the output shaft, but the planetary gear that meshes with the sun gear is not restricted in rotation. Therefore, both the sun gear and the planetary gear idle. Therefore, the rotation of the output shaft is not transmitted to the input shaft.
本発明のクラッチにあっては、入力軸の正・逆いずれの回転も出力軸に伝達され、入力軸の回転が正・逆いずれの方向であっても、出力軸が入力軸からの回転と同じ方向に回転した場合には、出力軸から入力軸への回転の伝達は遮断される。これにより、本発明のクラッチを正逆両方向に回転するモーターの保護を目的に使用した際には、２つのワンウェイクラッチを電子制御によって切り替えて使用する必要はなく、装置を単純なものにできてコストを削減することができる。 In the clutch of the present invention, both normal and reverse rotations of the input shaft are transmitted to the output shaft, and the rotation of the output shaft from the input shaft is independent of the normal and reverse rotations of the input shaft. When rotating in the same direction, the transmission of rotation from the output shaft to the input shaft is cut off. As a result, when the clutch of the present invention is used for the purpose of protecting the motor that rotates in both forward and reverse directions, it is not necessary to switch between the two one-way clutches by electronic control, and the device can be simplified. The cost can be reduced.
以下、図面に基づいて本発明のクラッチについて説明する。図１乃至３に、本発明のクラッチの実施例の全体構造を示す。図４乃至７に、主要構成部品を単体の状態で示す。図８に、本発明のクラッチの作動の説明図を示す。 Hereinafter, the clutch of the present invention will be described with reference to the drawings. 1 to 3 show the overall structure of an embodiment of the clutch of the present invention. 4 to 7 show the main components as a single unit. FIG. 8 shows an explanatory diagram of the operation of the clutch of the present invention.
図１に示すクラッチは、固定された断面略円形のハウジング２を備えており、このハウジング２内には、共通の回転軸（中心軸）ｏの周りに回転可能な入力軸４及び出力軸６が設けられている。ハウジング２内には更に、出力軸６に各々連結された２つの遊星歯車機構（第１遊星歯車機構８ａ及び第２遊星歯車機構８ｂ）と、これらが有する遊星歯車を夫々回転可能に軸支するキャリア１０とが配置されている。 The clutch shown in FIG. 1 includes a fixed housing 2 having a substantially circular cross section. In the housing 2, an input shaft 4 and an output shaft 6 rotatable about a common rotation axis (center axis) o. Is provided. Further, in the housing 2, two planetary gear mechanisms (first planetary gear mechanism 8a and second planetary gear mechanism 8b) respectively connected to the output shaft 6 and the planetary gears that these have are rotatably supported. The carrier 10 is arranged.
図１乃至３と共に図４を参照して説明すると、ハウジング２は、略円筒形状の周壁部１４と、円板形状の端板部１６とからなるカップ状部材であって、内側には略円柱形状の空間部１８が設けられている。周壁部１４の外周面にはハウジング２を固定するための凹状の取付溝２０が周方向に等角度間隔をおいて４つ形成されている。周壁部１４の開口側端面には円板形状のシールド体２２が圧入され、空間部１８は閉鎖される。ハウジング２の中心軸は入力軸４及び出力軸６の回転軸ｏと同一であり、端板部１６及びシールド体２２２には夫々円形の中央穴が形成されている。 Referring to FIG. 4 together with FIGS. 1 to 3, the housing 2 is a cup-shaped member including a substantially cylindrical peripheral wall portion 14 and a disc-shaped end plate portion 16, and has a substantially cylindrical shape inside. A space 18 having a shape is provided. On the outer peripheral surface of the peripheral wall portion 14, four concave mounting grooves 20 for fixing the housing 2 are formed at equal angular intervals in the circumferential direction. A disk-shaped shield body 22 is press-fitted into the opening-side end surface of the peripheral wall portion 14, and the space portion 18 is closed. The center axis of the housing 2 is the same as the rotation axis o of the input shaft 4 and the output shaft 6, and the end plate portion 16 and the shield body 222 are each formed with a circular center hole.
図１乃至３と共に図５を参照して説明すると、入力軸４は円板形状の基部２４と、基部２４の中央から軸方向片側に延びる軸部２６とを備え、中央には軸方向に貫通して延びる断面円形の穴２８が形成されている。軸部２６の断面は円環形状の外周面の一部を直線状に切り欠いた形状であって、軸部２６にはモーターのような図示しない適宜の駆動源が連結される。基部２４の外周面には押圧片３０が固着されている。図示の実施例においては、押圧片３０は直径方向に対向して２つ設けられており、押圧片３０の各々は、断面が扇形状であって、周方向両側が夫々矩形平面である。そして、押圧片３０の各々には後述する第１遊星歯車及び第２遊星歯車の自転を規制する規制手段３２が固着されている。規制手段３２は押圧片３０の中央において軸部２６とは反対側の軸方向に向かって直線状に延びている。図示の実施例においては、規制手段３２の断面は外歯歯車の径方向外側部を円弧状に切り欠いた形状であり、この外歯歯車の外側縁は図５の右図において押圧片３０の外側縁と面一である（図２及び３も参照されたい）。
出力軸６は断面円形の棒状部材であって、これがスライドドアや便座のような図示しない適宜の従動部材に適宜の方法によって連結される。
Referring to FIG. 5 together with FIGS. 1 to 3, the input shaft 4 includes a disk-shaped base portion 24 and a shaft portion 26 that extends from the center of the base portion 24 to one side in the axial direction. A hole 28 having a circular cross section is formed. A cross section of the shaft portion 26 has a shape in which a part of an outer peripheral surface of a ring shape is linearly cut out, and an appropriate driving source (not shown) such as a motor is connected to the shaft portion 26. A pressing piece 30 is fixed to the outer peripheral surface of the base portion 24. In the illustrated embodiment, two pressing pieces 30 are provided so as to face each other in the diametrical direction. Each pressing piece 30 has a fan-shaped cross section and both sides in the circumferential direction are rectangular flat surfaces. And, each of the pressing pieces 30 is fixed with a restricting means 32 for restricting rotation of a first planetary gear and a second planetary gear, which will be described later. The restricting means 32 extends linearly in the axial direction on the side opposite to the shaft portion 26 at the center of the pressing piece 30. In the illustrated embodiment, the restricting means 32 has a cross section in which the radially outer side portion of the external gear is cut out in an arc shape, and the outer edge of the external gear is the pressing piece 30 in the right view of FIG. It is flush with the outer edge (see also Figures 2 and 3).
The output shaft 6 is a rod-shaped member having a circular cross section, which is connected to an appropriate driven member (not shown) such as a slide door or a toilet seat by an appropriate method.
図１乃至３と共に図６を参照して説明すると、第１遊星歯車機構８ａ及び第２遊星歯車機構８ｂは共に、一方向クラッチ３６を介して出力軸６に連結される太陽歯車３８と、太陽歯車３８と噛み合う遊星歯車４０とを備えている。図示の実施例においては、上記一方向クラッチ、太陽歯車、及び遊星歯車は何れも第１遊星歯車機構８ａ及び第２遊星歯車機構８ｂにおいて共通部品であって、後述するとおり、配置する際の夫々の向きを入れ替えることによって第１遊星歯車機構８ａ又は第２遊星歯車機構８ｂのいずれかの構成部品となる。 Referring to FIG. 6 together with FIGS. 1 to 3, the first planetary gear mechanism 8 a and the second planetary gear mechanism 8 b are both a sun gear 38 connected to the output shaft 6 via a one-way clutch 36, and a sun gear 38. A planetary gear 40 meshing with the gear 38 is provided. In the illustrated embodiment, the one-way clutch, the sun gear, and the planetary gear are all common components in the first planetary gear mechanism 8a and the second planetary gear mechanism 8b, and as described later, they are respectively arranged. By changing the orientation of the above, it becomes a component of either the first planetary gear mechanism 8a or the second planetary gear mechanism 8b.
本実施例で用いられる一方向クラッチ３６は、出力軸６の周囲に配置された複数の楔形空間に、ばね４２で噛み込み方向に押されたローラー４４を設置したものであり、これは一方向クラッチとしては周知な形態であるため本明細書ではその詳細な説明を省略する。一方向クラッチ３６は太陽歯車３８の内側に嵌め込まれてこれと一体となる。そして、一方向クラッチ３６は、後述するとおり、ここに挿通される出力軸６の回転がローラー４４を楔の狭い方向へ移動させる場合には、ローラー４４が出力軸６との間で噛み込んで、太陽歯車３８を出力軸６と一体回転させる。一方、出力軸６の回転がローラー４４を楔の広い方向へ移動させる場合には、ローラー４４は出力軸６との間で噛み込まず、出力軸６は太陽歯車３８に対して空転する。遊星歯車４０には軸方向片側に向かって直線状に延びる筒壁４６が設けられている。筒壁４６の外径は遊星歯車４０のピッチ円直径よりも小さく、延出長さは太陽歯車３８の幅（つまり軸方向長さ）と実質上同一である。 The one-way clutch 36 used in the present embodiment is one in which the rollers 44 pressed in the biting direction by the spring 42 are installed in a plurality of wedge-shaped spaces arranged around the output shaft 6, which is one-way. Since the clutch is a well-known form, detailed description thereof will be omitted in this specification. The one-way clutch 36 is fitted inside the sun gear 38 to be integrated with it. Then, as will be described later, the one-way clutch 36 meshes with the output shaft 6 when the rotation of the output shaft 6 inserted therein moves the roller 44 in the narrow direction of the wedge. , The sun gear 38 is integrally rotated with the output shaft 6. On the other hand, when the rotation of the output shaft 6 moves the roller 44 in the wide direction of the wedge, the roller 44 does not engage with the output shaft 6 and the output shaft 6 idles with respect to the sun gear 38. The planetary gear 40 is provided with a cylindrical wall 46 extending linearly toward one side in the axial direction. The outer diameter of the cylinder wall 46 is smaller than the pitch circle diameter of the planetary gear 40, and the extension length is substantially the same as the width (that is, the axial length) of the sun gear 38.
図１乃至３と共に図７を参照して説明すると、キャリア１０は円環板状の基部４８を備えている。基部４８には入力軸４の押圧片３０が嵌り込む凹部５０が形成されている。図示の実施例においては、凹部５０は直径方向において対向して２つ形成されおり、凹部５０の各々は扇形状であって、周方向両側は夫々矩形平面（つまり押圧片３０の側面の形状と同一）である。基部４８における凹部５０の周方向両側にはこれと近接して、遊星歯車４０を軸支するキャリア軸５２が固着されている。図示の実施例においては、キャリア軸５２は周方向に等角度間隔をおいて４つ配置されている。基部４８には、キャリア軸５２と平行で、これよりも幾分長い支持片５４も固着されている。図示の実施例においては、支持片５４の断面は扇形状であって、直径方向に対向して２つ設けられている。キャリア１０は更にキャリア補助板５６を備えている。キャリア補助板５６の片側面には受け孔５８が形成されており、受け孔５８が支持片５４を軸受することで、基部４８とキャリア補助板５６とは軸方向に間隔をおいて対向して一体的に係合される。キャリア補助板５６の他側面には円環状の溝６０が形成されている。 Referring to FIG. 7 together with FIGS. 1 to 3, the carrier 10 includes an annular plate-shaped base portion 48. The base 48 has a recess 50 into which the pressing piece 30 of the input shaft 4 is fitted. In the illustrated embodiment, two recesses 50 are formed facing each other in the diametrical direction, each of the recesses 50 has a fan shape, and both sides in the circumferential direction are rectangular flat surfaces (that is, the shape of the side surface of the pressing piece 30). Same). A carrier shaft 52 that pivotally supports the planetary gear 40 is fixed to both sides of the base portion 48 in the circumferential direction of the concave portion 50 in close proximity thereto. In the illustrated embodiment, four carrier shafts 52 are arranged at equal angular intervals in the circumferential direction. A support piece 54, which is parallel to the carrier axis 52 and is slightly longer than the carrier axis 52, is also fixed to the base portion 48. In the illustrated embodiment, the support piece 54 has a fan-shaped cross section, and two support pieces 54 are provided to face each other in the diametrical direction. The carrier 10 further includes a carrier auxiliary plate 56. A receiving hole 58 is formed on one side surface of the carrier auxiliary plate 56, and the receiving hole 58 bears the support piece 54 so that the base portion 48 and the carrier auxiliary plate 56 face each other with an axial gap. Engaged together. An annular groove 60 is formed on the other side surface of the carrier auxiliary plate 56.
図１乃至３を参照して説明すると、上述した各構成部品は以下のような状態でハウジング２の空間部１８に収容される。
キャリア１０は、基部４８がハウジング２の端板部１６と接触するようにして配置される。入力軸４は、基部２４がキャリア１０の中央穴に嵌め合わされると共に押圧片３０がキャリア１０の基部４８に形成された凹部５０に嵌め合わされ、軸部２６がハウジング２の端板部１６を貫通する。第１遊星歯車機構８ａはハウジング２の端板部１６側、第２遊星歯車機構８ｂはハウジング２の開口端側に夫々軸方向に重ねて配置される（以下では、第１遊星歯車機構を構成する部品については「ａ」を、第２遊星歯車機構を構成する部品については「ｂ」を夫々番号の末尾に付して説明する）。このとき、一方向クラッチ３６ａ及び一方向クラッチ３６ｂが出力軸６の空転を許容する回転方向は相互に逆に設定される。つまり、一方向クラッチ３６ａはここに挿通される出力軸６が図１のＡ−Ａ断面図の左方から見て（つまり断面図Ｂ−Ｂにおいて）反時計方向に回転するときに出力軸６に対して空転し、一方向クラッチ３６ｂは出力軸６が図１のＡ−Ａ断面図の右方から見て（つまり断面図Ｃ−Ｃにおいて）反時計方向に回転するときに出力軸６に対して空転するように設定される。遊星歯車４０ａ及び遊星歯車４０ｂは、周方向に見て交互になるようにキャリア軸５２に挿通される。キャリア補助板５６は、キャリア１０の支持片５４の延出端部に受け孔５８が嵌め合わされて、キャリア１０と組み合わされ、第１遊星歯車機構８ａ及び第２遊星歯車機構８ｂはキャリア１０の基部４８とキャリア補助板５６とによって軸方向に支持される。そして、キャリア補助板５６の溝６０に環状の波ばね６２が嵌め込まれた状態で、シールド体２２が空間部１８に強制されこれを閉鎖する。そのため、キャリア１０にはキャリア補助板５６を介して波ばね６２による負荷が付加される。そして、出力軸６が中央に挿通される。
Explaining with reference to FIGS. 1 to 3, each component described above is accommodated in the space portion 18 of the housing 2 in the following state.
The carrier 10 is arranged such that the base portion 48 contacts the end plate portion 16 of the housing 2. In the input shaft 4, the base portion 24 is fitted in the central hole of the carrier 10, the pressing piece 30 is fitted in the recessed portion 50 formed in the base portion 48 of the carrier 10, and the shaft portion 26 penetrates the end plate portion 16 of the housing 2. To do. The first planetary gear mechanism 8a and the second planetary gear mechanism 8b are axially overlapped with each other on the end plate portion 16 side of the housing 2 and on the open end side of the housing 2 (hereinafter, the first planetary gear mechanism is configured. The description will be made by adding “a” to the parts to be added and “b” to the parts constituting the second planetary gear mechanism at the end of the numbers). At this time, the rotation directions in which the one-way clutch 36a and the one-way clutch 36b allow the output shaft 6 to idle are set to be opposite to each other. That is, the one-way clutch 36a is rotated when the output shaft 6 inserted through the one-way clutch 36a rotates counterclockwise when viewed from the left side of the AA sectional view of FIG. 1 (that is, in the sectional view BB). In contrast, the one-way clutch 36b rotates on the output shaft 6 when the output shaft 6 rotates counterclockwise when viewed from the right side of the AA sectional view of FIG. 1 (that is, in the sectional view CC). It is set so as to idle. The planetary gears 40a and the planetary gears 40b are inserted through the carrier shaft 52 so as to alternate in the circumferential direction. The carrier auxiliary plate 56 is combined with the carrier 10 by fitting the receiving hole 58 to the extended end portion of the support piece 54 of the carrier 10, and the first planetary gear mechanism 8a and the second planetary gear mechanism 8b are the base portions of the carrier 10. It is supported in the axial direction by 48 and the carrier auxiliary plate 56. Then, with the annular wave spring 62 fitted in the groove 60 of the carrier auxiliary plate 56, the shield body 22 is forced by the space portion 18 to close it. Therefore, a load is applied to the carrier 10 via the carrier auxiliary plate 56 by the wave spring 62. Then, the output shaft 6 is inserted through the center.
続いて、図１に示すクラッチの作動について、図８を参照して説明する。
図８において矢印で示すように、駆動源のモーターにより入力軸４がＡ−Ａ断面図の右方から見て時計方向に回転（以下これを正回転とする）すると、入力軸４に固着された押圧片３０も同一方向に回転し、押圧片３０がキャリア１０の凹部５０において基部４８と当接してこれを押す。このとき、第一遊星歯車機構８ａにあっては、断面図Ｂ−Ｂに示すとおり、押圧片３０に固着された規制手段３２が遊星歯車４０ａと噛み合い、遊星歯車４０ａの自転は規制され、入力軸４の回転が遊星歯車４０ａを介して太陽歯車３８ａに伝達される。太陽歯車３８ａと一体である一方向クラッチ３６ａが同断面図の矢印で示す方向に回転をすると、一方向クラッチ３６ａのローラー４４ａが出力軸６の外周面との間で噛み込み、一方向クラッチ３６ａと出力軸６とは相対回転不能となり一体で回転することとなる。換言すると、入力軸４の正回転は第一遊星歯車機構８ａを介して出力軸４に伝達される。
Next, the operation of the clutch shown in FIG. 1 will be described with reference to FIG.
As shown by the arrow in FIG. 8, when the input shaft 4 is rotated clockwise by the motor of the drive source when viewed from the right side of the AA sectional view (hereinafter, this is referred to as forward rotation), the input shaft 4 is fixed to the input shaft 4. The pressing piece 30 also rotates in the same direction, and the pressing piece 30 abuts against the base 48 in the recess 50 of the carrier 10 and presses it. At this time, in the first planetary gear mechanism 8a, as shown in the cross-sectional view BB, the restricting means 32 fixed to the pressing piece 30 meshes with the planetary gear 40a, and the rotation of the planetary gear 40a is restricted, so that the input force is reduced. The rotation of the shaft 4 is transmitted to the sun gear 38a via the planetary gear 40a. When the one-way clutch 36a, which is integral with the sun gear 38a, rotates in the direction shown by the arrow in the same sectional view, the roller 44a of the one-way clutch 36a is engaged with the outer peripheral surface of the output shaft 6, and the one-way clutch 36a. And the output shaft 6 cannot rotate relative to each other and thus rotate integrally. In other words, the positive rotation of the input shaft 4 is transmitted to the output shaft 4 via the first planetary gear mechanism 8a.
このとき、第二遊星歯車機構８ｂにあっては、断面図Ｃ−Ｃにおいて矢印で示すとおり、出力軸６と一方向クラッチ３６ｂとの間で噛み込みが生じて太陽歯車３８ｂが回転すると共に、これと噛み合う遊星歯車４０ｂも回転する。 At this time, in the second planetary gear mechanism 8b, as shown by the arrow in the cross-sectional view C-C, the sun gear 38b rotates due to engagement between the output shaft 6 and the one-way clutch 36b, and The planetary gear 40b meshing with this also rotates.
次に、入力軸４が正回転しているときに、出力軸６が入力軸４に対して正回転しようとする場合について説明する。この場合、第一遊星歯車機構８ａにあっては、図８の断面図Ｂ−Ｂに示すとおり、ローラー４４ａは出力軸６の外周面との噛み合いが解除される方向（つまり同断面図において反時計方向）へ移動されるため、出力軸６の回転が一方向クラッチ３６ａを介して入力軸４に伝達されることはない。第二遊星歯車機構８ｂにあっては、図８の断面図Ｃ−Ｃに示すとおり、ローラー４４ｂは出力軸６の外周面との噛み合いが生じる方向（つまり同断面図において時計方向）へ移動させられるが、太陽歯車３８ｂと噛み合う遊星歯車４０ｂは自転が規制されていないため、太陽歯車３８ｂ及び遊星歯車４０ｂは共に空転する。従って、出力軸６の回転が一方向クラッチ３６ｂを介して入力軸４に伝達されることはない。 Next, a case where the output shaft 6 tries to rotate forward with respect to the input shaft 4 while the input shaft 4 is rotating forward will be described. In this case, in the first planetary gear mechanism 8a, as shown in the sectional view BB of FIG. 8, the roller 44a is in the direction in which the meshing with the outer peripheral surface of the output shaft 6 is released (that is, in the sectional view of FIG. Since it is moved in the clockwise direction, the rotation of the output shaft 6 is not transmitted to the input shaft 4 via the one-way clutch 36a. In the second planetary gear mechanism 8b, as shown in the sectional view CC of FIG. 8, the roller 44b is moved in the direction in which the outer peripheral surface of the output shaft 6 is meshed (that is, the clockwise direction in the sectional view). However, since the rotation of the planetary gear 40b that meshes with the sun gear 38b is not restricted, the sun gear 38b and the planetary gear 40b both idle. Therefore, the rotation of the output shaft 6 is not transmitted to the input shaft 4 via the one-way clutch 36b.
入力軸４が逆回転した場合には、入力軸４の回転は第二遊星歯車機構８ｂを介して出力軸６に伝達される。全体的な作動は、入力軸４が正回転したときと同じであるので詳細な説明については省略する。入力軸４が逆回転しているときに、出力軸６が入力軸４に対して逆回転した場合も、出力軸６の回転が一方向クラッチ３６ａ及び３６ｂを介して入力軸４に伝達されることはない。 When the input shaft 4 rotates in the reverse direction, the rotation of the input shaft 4 is transmitted to the output shaft 6 via the second planetary gear mechanism 8b. The overall operation is the same as when the input shaft 4 rotates in the forward direction, and therefore detailed description will be omitted. Even when the output shaft 6 reversely rotates with respect to the input shaft 4 while the input shaft 4 is reversely rotating, the rotation of the output shaft 6 is transmitted to the input shaft 4 via the one-way clutches 36a and 36b. There is no such thing.
以上のことから、本発明のクラッチにあっては、入力軸４の正・逆いずれの回転も出力軸６に伝達される。そして、入力軸４の回転が正・逆いずれの方向であっても、出力軸６が入力軸４からの回転と同じ方向に相対回転した場合には、出力軸６から入力軸４への回転の伝達は遮断される。これにより、本発明のクラッチを正逆両方向に回転するモーターの保護を目的に使用した際には、２つのワンウェイクラッチを電子制御によって切り替えて使用する必要はなく、装置を単純なものにできてコストを削減することができる。 From the above, in the clutch of the present invention, both forward and reverse rotations of the input shaft 4 are transmitted to the output shaft 6. When the output shaft 6 relatively rotates in the same direction as the rotation from the input shaft 4 regardless of whether the rotation of the input shaft 4 is normal or reverse, the rotation from the output shaft 6 to the input shaft 4 is performed. Is cut off. As a result, when the clutch of the present invention is used for the purpose of protecting the motor that rotates in both forward and reverse directions, it is not necessary to switch between the two one-way clutches by electronic control, and the device can be simplified. The cost can be reduced.
以上詳述したように、本発明のクラッチは、出力軸に連結された２つの遊星歯車機構を軸方向に重ねて配置し、夫々の遊星歯車機構の太陽歯車は相互に反対方向に空転するよう設定された一方向クラッチを介して出力軸に連結され、入力軸が回転したときは、その回転方向に応じて、一方の遊星歯車機構が出力軸と一体となって回転すると共に他方の遊星歯車機構は出力軸に対して空転し、出力軸が入力軸からの回転と同じ方向に相対回転したときは、一方の遊星歯車機構の太陽歯車にのみ出力軸の回転が伝達されるが、出力軸の回転が伝達された太陽歯車と噛み合う遊星歯車が空転することで、入力軸への回転の伝達が遮断されるようにしたものである。 As described above in detail, in the clutch of the present invention, the two planetary gear mechanisms connected to the output shaft are arranged in an axially overlapping manner, and the sun gears of the respective planetary gear mechanisms rotate in opposite directions. When the input shaft rotates via the set one-way clutch and the input shaft rotates, one planetary gear mechanism rotates integrally with the output shaft and the other planetary gear according to the rotation direction. The mechanism idles with respect to the output shaft, and when the output shaft relatively rotates in the same direction as the rotation from the input shaft, the rotation of the output shaft is transmitted only to the sun gear of one planetary gear mechanism. When the planetary gear that meshes with the sun gear to which the rotation is transmitted idles, the transmission of the rotation to the input shaft is blocked.
本発明は上述した実施例に限定されるものではなく、本発明の範囲を逸脱することなく種々の変形乃至修正が可能である。例えば、上述した実施例においては、規制手段は外歯歯車の一部を切り取った形状であったが、これに替えて、円弧状部材の周方向両側端にのみ外歯を設けた形状（図９（ａ））や、遊星歯車に噛み込むピン（図９（ｂ））であってもよい。 The present invention is not limited to the above-described embodiments, and various changes and modifications can be made without departing from the scope of the present invention. For example, in the above-described embodiments, the restricting means has a shape in which a part of the external gear is cut out, but instead of this, a shape in which external teeth are provided only at both circumferential ends of the arcuate member (see FIG. 9(a)) or a pin (FIG. 9(b)) that engages with the planetary gear.
２：ハウジング
４：入力軸
６：出力軸
８ａ及び８ｂ：第一遊星歯車機構及び第二遊星歯車機構
１０：キャリア
３０：押圧片
３２：規制手段
３６ａ及び３６ｂ：一方向クラッチ
３８ａ及び３８ｂ：太陽歯車
４０ａ及び４０ｂ：遊星歯車
５６：キャリア補助板
2: housing 4: input shaft 6: output shaft 8a and 8b: first planetary gear mechanism and second planetary gear mechanism 10: carrier 30: pressing piece 32: restricting means 36a and 36b: one-way clutch 38a and 38b: sun gear 40a and 40b: Planetary gear 56: Carrier auxiliary plate
Claims (4)
前記２つの遊星歯車機構は夫々軸方向に重ねて配置され、前記出力軸に一方向クラッチを介して連結された太陽歯車、及び前記太陽歯車と噛み合う遊星歯車を備え、前記２つの遊星歯車機構の太陽歯車に配設された一方向クラッチの各々は前記出力軸に対して相互に反対の回転方向で空転するよう設定され、前記２つの遊星歯車機構の遊星歯車は夫々前記共通の中心軸の周りを回転可能な共通のキャリアによって回転可能に軸支されており、
前記入力軸には押圧片が固着されると共に前記キャリアには前記押圧片が嵌り込む凹部が形成され、前記２つの遊星歯車機構の遊星歯車は前記凹部の周方向両側に相互に配置され、前記押圧片には前記遊星歯車の自転を規制する規制手段が固着されており、
前記入力軸が回転したときは、その回転方向に応じて、前記規制手段が前記２つの遊星歯車機構のいずれか一方の遊星歯車の自転を規制すると共に、前記押圧片が前記凹部で前記キャリアと当接してこれを周方向に押し、前記２つの遊星歯車機構が前記出力軸と一体となって回転し、
前記出力軸が前記入力軸からの回転と同じ方向に回転したときは、前記２つの遊星歯車機構の太陽歯車のうち、自転が規制されていない遊星歯車と噛み合う太陽歯車に前記出力軸の回転が伝達されるが、前記出力軸の回転が伝達された前記太陽歯車と噛み合う前記遊星歯車は空転し、前記出力軸から前記入力軸への回転の伝達は遮断される、ことを特徴とするクラッチ。 An input shaft and an output shaft rotatable about a common central axis, and two planetary gear mechanisms connected to the output shaft,
The two planetary gear mechanisms are arranged in the axial direction so as to be overlapped with each other, and include a sun gear connected to the output shaft via a one-way clutch, and a planetary gear that meshes with the sun gear. Each of the one-way clutches arranged on the sun gear is set so as to idle in mutually opposite rotational directions with respect to the output shaft, and the planetary gears of the two planetary gear mechanisms respectively rotate around the common central axis. Is rotatably supported by a common carrier that can rotate
A pressing piece is fixed to the input shaft and a recess into which the pressing piece is fitted is formed in the carrier, and the planet gears of the two planetary gear mechanisms are arranged on both sides in the circumferential direction of the recess, and A restraint means for restraining rotation of the planetary gear is fixed to the pressing piece,
When the input shaft rotates, the restricting means restricts the rotation of one of the planetary gears of the two planetary gear mechanisms in accordance with the rotation direction of the input shaft, and the pressing piece serves as the carrier in the recess. Abutting and pushing it in the circumferential direction, the two planetary gear mechanisms rotate integrally with the output shaft,
When the output shaft rotates in the same direction as the rotation from the input shaft, the rotation of the output shaft occurs in the sun gear of the two planetary gear mechanisms that meshes with the planet gear whose rotation is not restricted. Although transmitted, the planetary gear meshing with the sun gear to which the rotation of the output shaft is transmitted idles, and transmission of rotation from the output shaft to the input shaft is cut off.
前記支持片は、前記キャリアと一体的に結合されるキャリア補助板によって軸受され、前記基部と前記キャリア補助板とは軸方向に間隔をおいて対向する、請求項１乃至３のいずれかに記載のクラッチ。 The carrier includes a plate-shaped base portion and a support piece extending in the axial direction from the base portion,
The said support piece is supported by the carrier auxiliary|assistant board integrally couple|bonded with the said carrier, The said base part and the said carrier auxiliary|assistant board oppose with the space|interval in the axial direction, The statement in any one of Claim 1 thru|or 3. Clutch.
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