JP2019143313A - Drive force transmission device and shading device using the same - Google Patents

Drive force transmission device and shading device using the same Download PDF

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JP2019143313A
JP2019143313A JP2018026438A JP2018026438A JP2019143313A JP 2019143313 A JP2019143313 A JP 2019143313A JP 2018026438 A JP2018026438 A JP 2018026438A JP 2018026438 A JP2018026438 A JP 2018026438A JP 2019143313 A JP2019143313 A JP 2019143313A
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rotation
force transmission
transmission device
driving force
carrier
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JP7002362B2 (en
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慶弘 ▲高▼山
慶弘 ▲高▼山
Yoshihiro Takayama
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Tachikawa Blind Manufacturing Co Ltd
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Tachikawa Blind Manufacturing Co Ltd
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Abstract

To provide a drive force transmission device capable of outputting rotation responsive to input rotation, the output rotation having different transmission gear ratios at immediately after input start and after that.SOLUTION: According to the present invention, there is provided a drive force transmission device comprising a first member, a second member, and a third member, where input rotation to the first member is output as rotation of the second member. The drive force transmission device is configured so that at least either of the second member and the third member rotates due to rotation of the first member; and comprises a rotation regulation member that switches regulation and permission of the third member's rotation.SELECTED DRAWING: Figure 3

Description

本発明は、入力回転に対し、複数の変速比の回転を出力する駆動力伝達装置と、当該駆動力伝達装置を用いた遮蔽装置に関する。   The present invention relates to a driving force transmission device that outputs a plurality of gear ratio rotations with respect to an input rotation, and a shielding device that uses the driving force transmission device.

従来、遮蔽装置の１つである横型ブラインドには、操作コードの操作により巻取軸を回転駆動して、スラットを昇降及び角度調節可能としたものがある（特許文献１参照）。このものは、巻取軸から昇降コードを繰り出すことによりスラットが下降され、巻取軸に昇降コードを巻取ることによりスラットが引き上げられる。また、スラットの昇降動作が始まる前には、スラットが回動され、各スラットは全閉状態又は逆全閉状態まで回動された状態で昇降するようになっている。   2. Description of the Related Art Conventionally, there is a horizontal blind, which is one of shielding devices, that allows a winding shaft to be rotationally driven by operating an operation cord so that a slat can be lifted and adjusted (see Patent Document 1). In this device, the slat is lowered by feeding the lifting / lowering cord from the winding shaft, and the slat is pulled by winding the lifting / lowering cord on the winding shaft. Moreover, before the raising / lowering operation | movement of a slat starts, a slat is rotated and each slat raises / lowers in the state rotated to the fully closed state or the reverse fully closed state.

特開２０１４−２２１９７０号公報JP 2014-221970 A

ところで、スラットの昇降動作における初動において各スラットを回動させるときに、巻取軸を回転させる操作の速度が過度に速いと、スラットの回動不足が生じることがある。すなわち、巻取軸の回転させる操作の速度が過度に速いと、それに伴うラダーコードの移動に対してスラットの回動が追従できないことがある。このようなスラットの追従不足は、美観を損ねる。このような問題は、操作コードの操作による巻取軸の回転が一定であることに起因する。   By the way, when each slat is rotated in the initial movement in the raising and lowering operation of the slat, if the operation speed for rotating the winding shaft is excessively high, the slat may be insufficiently rotated. That is, if the speed of the operation for rotating the winding shaft is excessively high, the rotation of the slats may not be able to follow the movement of the ladder cord. Such insufficient tracking of the slats detracts from aesthetics. Such a problem is caused by the fact that the rotation of the winding shaft by the operation of the operation cord is constant.

また、上記横型ブラインドの例に限らず、様々な場面において、入力回転に対して、初動とその後の動作で回転速度を変化させたいという課題が生じていた。   In addition to the horizontal blind example described above, in various scenes, there has been a problem that it is desired to change the rotational speed between the initial movement and the subsequent movement with respect to the input rotation.

本発明はこのような事情に鑑みてなされたものであり、入力回転に対し、入力開始直後とその後で異なる変速比の回転を出力することの可能な駆動力伝達装置を提供するものである。   The present invention has been made in view of such circumstances, and provides a driving force transmission device capable of outputting a rotation with a different gear ratio immediately after the start of input and thereafter with respect to the input rotation.

本発明によれば、第１部材と、第２部材と、第３部材とを備え、前記第１部材への入力回転を前記第２部材の回転として出力する駆動力伝達装置であって、前記第１部材の回転に伴って前記第２部材と前記第３部材の少なくとも一方が回転するよう構成されており、前記第３部材の回転の規制と許容とを切り替える回転規制部材を備える、駆動力伝達装置が提供される。   According to the present invention, there is provided a driving force transmission device that includes a first member, a second member, and a third member, and that outputs input rotation to the first member as rotation of the second member, A driving force including a rotation restricting member configured to rotate at least one of the second member and the third member in accordance with the rotation of the first member, and to switch between restricting and allowing the rotation of the third member. A transmission device is provided.

本発明によれば、回転規制部材が第３部材の回転の規制と許容とを切り替える構成となっていることから、第３部材の回転状態が変化することで第１部材への入力に対する第２部材から出力する回転の状態を変化させることが可能となっている。   According to the present invention, since the rotation restricting member is configured to switch between restricting and allowing the rotation of the third member, the second state with respect to the input to the first member is changed by changing the rotation state of the third member. It is possible to change the state of rotation output from the member.

好ましくは、前記回転規制部材が前記第３部材の回転の規制と許容とを切り替えることで、前記第２部材の出力する回転の変速比が切り替わるよう構成される。   Preferably, the rotation restricting member switches between restricting and permitting the rotation of the third member, so that the rotation speed ratio output by the second member is switched.

好ましくは、前記回転規制部材は、前記第３部材に与える回転抵抗を変化させることで、前記第３部材の回転の規制と許容とを切り替えるよう構成される。   Preferably, the rotation restriction member is configured to switch between restriction and allowance of rotation of the third member by changing a rotation resistance applied to the third member.

好ましくは、前記回転規制部材は、前記第３部材の回転に伴って回転抵抗が増大することで前記第３部材の回転を規制し、前記第２部材の回転に伴って前記回転抵抗が低減されることで前記第３部材の回転を許容するよう構成される。   Preferably, the rotation restricting member restricts the rotation of the third member by increasing the rotation resistance with the rotation of the third member, and the rotation resistance is reduced with the rotation of the second member. Thus, the third member is configured to be allowed to rotate.

好ましくは、前記第１部材が回転開始後所定角度回転するまでは、前記回転規制部材が前記第３部材の回転を規制するとともに前記第２部材が第１の変速比で回転を出力し、前記第１部材が前記所定角度回転した後は、前記回転規制部材が前記第３部材の回転の規制を解除するとともに前記第１部材、前記第２部材及び前記第３部材が一体回転して、前記第２部材が第２の変速比で回転を出力するよう構成される。
好ましくは、前記第２部材は円周方向の一部の位置に第２部材係合部を備え、前記第３部材は、円周方向の一部の位置に第３部材係合部を備えており、前記第２部材係合部と前記第３部材係合部が前記回転規制部材に対して逆方向に作用することによって前記第３部材の回転の規制と許容が切り替わるよう構成される。 Preferably, the rotation restricting member restricts the rotation of the third member and the second member outputs the rotation at the first gear ratio until the first member rotates by a predetermined angle after the rotation starts. After the first member rotates the predetermined angle, the rotation restricting member releases the restriction of the rotation of the third member, and the first member, the second member, and the third member rotate integrally, The second member is configured to output rotation at the second gear ratio.
Preferably, the second member includes a second member engaging portion at a partial position in the circumferential direction, and the third member includes a third member engaging portion at a partial position in the circumferential direction. In addition, the second member engaging portion and the third member engaging portion act in opposite directions with respect to the rotation restricting member, so that the restriction and allowance of the rotation of the third member are switched.

好ましくは、前記第１部材、前記第２部材、前記第３部材及び前記回転規制部材を収容するケース部材と、前記ケース部材に固定された円筒状のカラーとを備え、前記回転規制部材は、前記カラーの外周面又は内周面に配置され且つ径方向に延びる突起を有するコイルスプリングを備えており、前記第３部材係合部は、前記第３部材の回転により前記コイルスプリングが縮径又は拡径して前記カラーに対して相対回転不能となるよう前記突起を押圧する位置に配置され、前記第２部材係合部は、前記第２部材の回転により前記コイルスプリングが前記カラーに対して相対回転可能となるよう前記突起を押圧する位置に配置される。   Preferably, the first member, the second member, the third member and a case member that accommodates the rotation restriction member, and a cylindrical collar fixed to the case member, the rotation restriction member, A coil spring disposed on an outer peripheral surface or an inner peripheral surface of the collar and having a protrusion extending in a radial direction, and the third member engaging portion is configured such that the diameter of the coil spring is reduced by rotation of the third member; The second member engaging portion is disposed at a position where the protrusion is pressed so that the diameter is increased and the relative rotation with respect to the collar becomes impossible. It arrange | positions in the position which presses the said protrusion so that relative rotation is possible.

好ましくは、遊星歯車機構を備え、前記第１部材、前記第２部材及び前記第３部材は、前記遊星歯車機構の太陽歯車部材、キャリア及び内歯車部材によって構成される。   Preferably, a planetary gear mechanism is provided, and the first member, the second member, and the third member are constituted by a sun gear member, a carrier, and an internal gear member of the planetary gear mechanism.

好ましくは、前記第１部材を前記太陽歯車部材とし、前記第２部材を前記キャリアとし、前記第３部材を前記内歯車部材とする。   Preferably, the first member is the sun gear member, the second member is the carrier, and the third member is the internal gear member.

また、本発明によれば、遮蔽部材と、前記遮蔽部材を開閉させる開閉コードと、操作部の操作により回転する入力軸と、入力軸の回転に伴って回転して前記開閉コードの巻取り及び巻戻しを行う巻取軸とを備え、前記巻取軸の回転と連動して前記遮蔽部材の角度を変更可能に構成された遮蔽装置であって、上記駆動力伝達装置を備え、前記駆動力伝達装置は、前記入力軸の回転を前記巻取軸に伝達するよう構成される、遮蔽装置が提供される。   Further, according to the present invention, the shielding member, the opening / closing cord for opening / closing the shielding member, the input shaft rotated by the operation of the operation unit, and the winding of the opening / closing cord rotating with the rotation of the input shaft A shielding device configured to change the angle of the shielding member in conjunction with rotation of the winding shaft, the driving force transmitting device, and the driving force A transmission device is provided that is configured to transmit rotation of the input shaft to the take-up shaft.

本発明の実施形態に係る横型ブラインドの正面図である。It is a front view of the horizontal blind concerning the embodiment of the present invention. 図１の横型ブラインドの駆動力伝達装置１０の分解斜視図である。It is a disassembled perspective view of the driving force transmission apparatus 10 of the horizontal blind of FIG. 図２の駆動力伝達装置１０の、図２とは異なる方向から見た場合の分解斜視図である。FIG. 3 is an exploded perspective view of the driving force transmission device 10 of FIG. 2 when viewed from a direction different from FIG. 2. 図２の駆動力伝達装置１０の、ケース部材２０を外した際の側面図である。FIG. 3 is a side view of the driving force transmission device 10 of FIG. 2 when a case member 20 is removed. 図２の駆動力伝達装置１０の、ケース部材２０以外の部材を組み立てた状態の斜視図である。FIG. 3 is a perspective view of the driving force transmission device 10 of FIG. 2 in a state where members other than the case member 20 are assembled. 図４のＡ−Ａ線における断面図である。It is sectional drawing in the AA of FIG. 図４のＢ−Ｂ線における断面図である。It is sectional drawing in the BB line of FIG. 図２の駆動力伝達装置１０の動作を説明するタイミングチャートである。3 is a timing chart for explaining the operation of the driving force transmission device 10 of FIG. 2. 図９Ａ〜図９Ｄは、図４のＢ−Ｂ線の断面における、動作説明図である。9A to 9D are operation explanatory diagrams in a cross section taken along line BB in FIG. 図１０Ａ〜図１０Ｄは、図１の横型ブラインドのスラット３の回動動作を示す説明図である。FIGS. 10A to 10D are explanatory views showing the rotation operation of the slat 3 of the horizontal blind in FIG. 遊星歯車機構Ｓの太陽歯車部材３０、キャリア４０及び内歯車部材５０の役割の組み合わせを示す表である。4 is a table showing combinations of roles of the sun gear member 30, the carrier 40, and the internal gear member 50 of the planetary gear mechanism S.

以下、本発明の実施形態について説明する。以下の実施形態中で示した各特徴は、互いに組み合わせ可能である。また、各特徴について独立して発明が成立する。   Hereinafter, embodiments of the present invention will be described. Each feature shown in the following embodiments can be combined with each other. The invention is established independently for each feature.

（１）構成の説明
（１−１）横型ブラインド全体の構成
図１に示す本発明の一実施形態に係る遮蔽装置である横型ブラインドは、ヘッドボックス１から垂下される複数本のラダーコード２（スラット支持コード）によって遮蔽部材としてのスラット３が支持され、ラダーコード２の下端にはボトムレール４が接続されている。ラダーコード２の近傍には、ヘッドボックス１から開閉コードとしての複数本の昇降コード５が垂下されている。昇降コード５の上端部はヘッドボックス１内に配設される巻取コーン６に巻着され、下端部はボトムレール４を支持している。 (1) Description of Configuration (1-1) Overall Configuration of Horizontal Blind A horizontal blind, which is a shielding device according to an embodiment of the present invention shown in FIG. 1, includes a plurality of ladder cords 2 suspended from a head box 1 ( A slat 3 as a shielding member is supported by a slat support cord), and a bottom rail 4 is connected to the lower end of the ladder cord 2. In the vicinity of the ladder cord 2, a plurality of lifting cords 5 as hanging cords are suspended from the head box 1. The upper end portion of the lifting / lowering cord 5 is wound around a winding cone 6 disposed in the head box 1, and the lower end portion supports the bottom rail 4.

ヘッドボックス１の一端部には昇降装置７が設けられており、昇降装置７から垂下される操作部としての無端状の操作コード８が操作されると、ヘッドボックス１内に配設される角軸状の入力軸９がまず回転し、駆動力伝達装置１０を介して角軸状の巻取軸としての角軸状の昇降軸１１が回転する。そして、昇降軸１１の回転に応じて巻取コーン６が回転し、昇降コード５を巻取りあるいは巻戻すことでスラット３が昇降するよう構成される。なお、昇降装置７は、操作コード８の操作をやめた際に自重によるスラット３の降下を防止する公知のストッパ機構（図示せず）を備えている。   A lifting device 7 is provided at one end of the head box 1, and when an endless operation cord 8 as an operation unit suspended from the lifting device 7 is operated, a corner disposed in the head box 1. The shaft-shaped input shaft 9 is first rotated, and the rectangular shaft-shaped lifting shaft 11 serving as the rectangular shaft-shaped winding shaft is rotated via the driving force transmission device 10. And the winding cone 6 rotates according to rotation of the raising / lowering axis | shaft 11, and it is comprised so that the slat 3 may raise / lower by winding up or rewinding the raising / lowering cord 5. FIG. The lifting device 7 includes a known stopper mechanism (not shown) that prevents the slat 3 from being lowered due to its own weight when the operation of the operation cord 8 is stopped.

また、ヘッドボックス１内には、スラット３の角度を調整する角度調整機構１２が設けられており、ラダーコード２の上端は角度調整機構１２が備えるチルトドラム（図示せず）に取着されている。角度調整機構１２は、クラッチ装置（図示せず）を備え、昇降軸１１の回転が選択的にチルトドラムに伝達されるよう構成されている。そして、操作コード８の操作開始から昇降軸１１が一定量回転する間、チルトドラムが回転してラダーコード２の前後のコードが互いに上下逆の方向に動作することで、各スラット３が同位相で角度調節されるようになっている。角度調整機構１２については、既知の任意の構成を適用することができるため、詳細な説明を省略する。   In addition, an angle adjustment mechanism 12 that adjusts the angle of the slat 3 is provided in the head box 1, and the upper end of the ladder cord 2 is attached to a tilt drum (not shown) provided in the angle adjustment mechanism 12. Yes. The angle adjustment mechanism 12 includes a clutch device (not shown), and is configured to selectively transmit the rotation of the elevating shaft 11 to the tilt drum. The tilt drum rotates and the cords before and after the ladder cord 2 operate in the opposite directions while the elevating shaft 11 rotates by a certain amount from the operation start of the operation cord 8, so that each slat 3 is in the same phase. The angle can be adjusted with. As the angle adjusting mechanism 12, any known configuration can be applied, and thus detailed description thereof is omitted.

ここで、駆動力伝達装置１０は、入力軸９の回転を、入力開始直後とその後で異なる変速比で出力するものである。以下に、図２〜図９を用いて、駆動力伝達装置１０の構成について説明する。なお、以下では、駆動力伝達装置１０の向きについて、入力する側を前側、出力する側を後側とする。また、本実施形態において、駆動力伝達装置１０は、ヘッドボックス１の長手方向の向きについて、昇降装置７が設けられる側（図１の正面図における右側）が前側、これと反対側（図１の左側）が後側となるよう設置される。   Here, the driving force transmission device 10 outputs the rotation of the input shaft 9 at a different gear ratio immediately after the start of input and thereafter. Below, the structure of the driving force transmission apparatus 10 is demonstrated using FIGS. In the following, regarding the direction of the driving force transmission device 10, the input side is the front side, and the output side is the rear side. Further, in the present embodiment, the driving force transmission device 10 has the front side on the side where the lifting device 7 is provided (the right side in the front view of FIG. 1) and the opposite side (FIG. 1). The left side) is the rear side.

（１−２）駆動力伝達装置１０の構成
駆動力伝達装置１０は、図２及び図３に示すように、前ケース２１及び後ケース２２からなるケース部材２０に、第１部材としての太陽歯車部材３０と、第２部材としてのキャリア４０と、第３部材としての内歯車部材５０と、４つの遊星歯車部材６０と、回転規制部材としてのコイルスプリング７０及びカラー８０とが収容されて構成される。なお、本実施形態において、コイルスプリング７０及びカラー８０は金属製とされ、その他の部材は樹脂製とされる。本実施形態の駆動力伝達装置１０は、太陽歯車部材３０に入力された回転を、キャリア４０の回転として出力するものである。具体的には、太陽歯車部材３０と入力軸９、キャリアと昇降軸１１が接続されることで、入力軸９の回転を２つのモードの異なる変速比で出力するものである。以下、各部材ごとに説明する。 (1-2) Configuration of Driving Force Transmission Device 10 As shown in FIGS. 2 and 3, the driving force transmission device 10 includes a sun gear as a first member in a case member 20 including a front case 21 and a rear case 22. The member 30, the carrier 40 as the second member, the internal gear member 50 as the third member, the four planetary gear members 60, the coil spring 70 and the collar 80 as the rotation restricting members are accommodated. The In the present embodiment, the coil spring 70 and the collar 80 are made of metal, and the other members are made of resin. The driving force transmission device 10 of the present embodiment outputs the rotation input to the sun gear member 30 as the rotation of the carrier 40. Specifically, the sun gear member 30 and the input shaft 9, and the carrier and the lifting shaft 11 are connected to output the rotation of the input shaft 9 at different gear ratios in the two modes. Hereinafter, each member will be described.

＜ケース部材２０＞
ケース部材２０は、図２〜図４に示すように、前側に配置される前ケース２１と後側に配置される後ケース２２とからなる。前ケース２１は、略矩形状の板状部２３と、当該板状部２３の上端及び下端から後方に向かって延びる一対の係合突起２４ａ，２４ｂを備える。板状部２３の中央には、貫通孔２１ａが形成されている。 <Case member 20>
As shown in FIGS. 2 to 4, the case member 20 includes a front case 21 disposed on the front side and a rear case 22 disposed on the rear side. The front case 21 includes a substantially rectangular plate-like portion 23 and a pair of engagement protrusions 24a and 24b extending rearward from the upper and lower ends of the plate-like portion 23. A through hole 21 a is formed at the center of the plate-like portion 23.

後ケース２２は、略矩形の底壁部２５及び、底壁部２５の外縁から前方向に向かって延びる側壁部２６を備えた略直方体形状の部材であり、これら底壁部２５及び側壁部２６によって筒状の収容空間２７を形成している。収容空間２７には、内歯車部材５０を保持する円柱状の大収容空間２７ａと、カラー８０を収容する大収容空間２７ａよりも小径である円柱状の小収容空間２７ｂとが前後方向に連続するように形成される。また、小収容空間２７ｂの外周の対向する２箇所には、底壁部２５から前方に向かって突起２７ｃが形成されている。加えて、収容空間２７の上下には、前ケース２１の係合突起２４ａ，２４ｂと係合する係合溝２８ａ，２８ｂが形成されている。そして、底壁部２５の中央には、貫通孔２５ａが形成されている。   The rear case 22 is a substantially rectangular parallelepiped member having a substantially rectangular bottom wall portion 25 and a side wall portion 26 extending forward from the outer edge of the bottom wall portion 25, and the bottom wall portion 25 and the side wall portion 26. Thus, a cylindrical accommodation space 27 is formed. In the accommodation space 27, a cylindrical large accommodation space 27 a that holds the internal gear member 50 and a cylindrical small accommodation space 27 b that has a smaller diameter than the large accommodation space 27 a that accommodates the collar 80 are continuous in the front-rear direction. Formed as follows. In addition, protrusions 27c are formed forward from the bottom wall portion 25 at two opposing locations on the outer periphery of the small accommodating space 27b. In addition, engaging grooves 28 a and 28 b that engage with the engaging protrusions 24 a and 24 b of the front case 21 are formed above and below the accommodation space 27. A through hole 25 a is formed in the center of the bottom wall portion 25.

＜太陽歯車部材３０＞
太陽歯車部材３０は、前方から順に入力側接続部３１、外周に亘って外歯３２ｇが形成される太陽ギア部３２及び円筒部３３を備える筒状の部材であり、駆動力伝達装置１０において回転が入力される部材である。入力側接続部３１が入力軸９と接続される。太陽歯車部材３０は、遊星歯車機構Ｓを構成する部材であり、太陽ギア部３２が４つの遊星歯車部材６０それぞれと歯合するよう構成される。 <Sun gear member 30>
The sun gear member 30 is a cylindrical member including an input side connection portion 31 in order from the front, a sun gear portion 32 in which external teeth 32 g are formed over the outer periphery, and a cylindrical portion 33. Is a member to be input. The input side connection unit 31 is connected to the input shaft 9. The sun gear member 30 is a member constituting the planetary gear mechanism S, and the sun gear portion 32 is configured to mesh with each of the four planetary gear members 60.

＜キャリア４０＞
キャリア４０は、遊星歯車機構Ｓを構成する部材であり、前キャリア部材４１及び後キャリア部材４２から構成される。前キャリア部材４１は、前方から順に、前円筒部４３と、前円筒部４３よりも径の大きい円盤部４４と、円盤部４４から後方に延びる４つの支持柱４５とを備える。前円筒部４３及び円盤部４４の中央には、太陽歯車部材３０の入力側接続部３１を相対回転可能に保持する貫通孔４１ａが形成される。また、４つの支持柱４５は円周方向に亘って等間隔に設けられ、各支持柱４５の先端（後端）には突起４５ａが設けられている。加えて、円盤部４４には、後キャリア部材４２の遊星歯車保持軸４８の先端（前端）に設けられた突起４８ａと嵌合する４つの嵌合孔４４ａが、４つの支持柱４５と交互に形成される。 <Carrier 40>
The carrier 40 is a member that constitutes the planetary gear mechanism S, and includes a front carrier member 41 and a rear carrier member 42. The front carrier member 41 includes, in order from the front, a front cylindrical portion 43, a disk portion 44 having a larger diameter than the front cylindrical portion 43, and four support columns 45 extending rearward from the disk portion 44. A through hole 41 a that holds the input side connection portion 31 of the sun gear member 30 so as to be relatively rotatable is formed in the center of the front cylindrical portion 43 and the disc portion 44. The four support columns 45 are provided at equal intervals in the circumferential direction, and a protrusion 45 a is provided at the front end (rear end) of each support column 45. In addition, the disk portion 44 has four fitting holes 44 a that are fitted with protrusions 48 a provided at the tip (front end) of the planetary gear holding shaft 48 of the rear carrier member 42, alternately with the four support columns 45. It is formed.

後キャリア部材４２は、円盤部４６及び後円筒部４７を前方からこの順に備え、加えて、円盤部４６から前方に延びる４つの遊星歯車保持軸４８を備える。４つの遊星歯車保持軸４８は円周方向に亘って等間隔に設けられ、各遊星歯車保持軸４８の先端（前端）には突起４８ａが設けられている。円盤部４６には、前キャリア部材４１の支持柱４５に設けられた突起４５ａと嵌合する４つの嵌合孔４６ａが、４つの遊星歯車保持軸４８と交互に形成される。また、円盤部４６の内周面は、太陽歯車部材３０の円筒部３３を相対回転可能に保持する保持部４６ｂとなっている。一方、後円筒部４７の内周面には、出力軸である昇降軸１１と接続する出力側接続部４７ａが形成される。加えて、後円筒部４７の径方向外側には、円周方向の一部の位置に、円盤部４６から後円筒部４７後端近傍に亘って延びるキャリア突起４９が形成されている。本実施形態においては、キャリア突起４９が本発明における第２部材係合部に対応する。キャリア突起４９の回転軸と垂直な方向の断面は、図７に示すように、扇形である。   The rear carrier member 42 includes a disk portion 46 and a rear cylindrical portion 47 in this order from the front, and further includes four planetary gear holding shafts 48 extending forward from the disk portion 46. The four planetary gear holding shafts 48 are provided at equal intervals in the circumferential direction, and a protrusion 48 a is provided at the tip (front end) of each planetary gear holding shaft 48. In the disk portion 46, four fitting holes 46 a for fitting with the protrusions 45 a provided on the support pillar 45 of the front carrier member 41 are formed alternately with the four planetary gear holding shafts 48. Moreover, the inner peripheral surface of the disk part 46 becomes the holding part 46b which hold | maintains the cylindrical part 33 of the sun gear member 30 so that relative rotation is possible. On the other hand, on the inner peripheral surface of the rear cylindrical portion 47, an output side connecting portion 47a that is connected to the elevating shaft 11 that is an output shaft is formed. In addition, a carrier protrusion 49 extending from the disk portion 46 to the vicinity of the rear end of the rear cylindrical portion 47 is formed at a part of the circumferential direction on the radially outer side of the rear cylindrical portion 47. In the present embodiment, the carrier protrusion 49 corresponds to the second member engaging portion in the present invention. The cross section of the carrier protrusion 49 in the direction perpendicular to the rotation axis is a fan shape as shown in FIG.

＜内歯車部材５０＞
内歯車部材５０は、遊星歯車機構Ｓを構成する部材であり、前方から順に、薄肉筒状部５１と狭径部５２とを備える。薄肉筒状部５１の内面には、円周方向に亘って、遊星歯車部材６０と歯合する内歯部５３が形成される。狭径部５２の内径は、後キャリア部材４２の後円筒部４７及びキャリア突起４９を挿入可能な大きさとされる。狭径部５２後端からは、円周方向の一部の位置に、後方に向かって延びる内歯車突起５４が形成されている。内歯車突起５４の回転軸と垂直な方向の断面は、図７に示すように、扇形であり、また、内歯車突起５４は、狭径部５２の内縁から径方向内側にも突出していて、キャリア突起４９と係合可能となっている。本実施形態においては、内歯車突起５４が本発明における第３部材係合部に対応する。 <Internal gear member 50>
The internal gear member 50 is a member constituting the planetary gear mechanism S, and includes a thin cylindrical portion 51 and a narrow-diameter portion 52 in order from the front. An inner tooth portion 53 that meshes with the planetary gear member 60 is formed on the inner surface of the thin cylindrical portion 51 in the circumferential direction. The inner diameter of the narrow diameter portion 52 is set such that the rear cylindrical portion 47 and the carrier protrusion 49 of the rear carrier member 42 can be inserted. From the rear end of the narrow diameter portion 52, an internal gear projection 54 extending rearward is formed at a part of the circumferential direction. As shown in FIG. 7, the cross section in the direction perpendicular to the rotation axis of the internal gear protrusion 54 has a fan shape, and the internal gear protrusion 54 also protrudes radially inward from the inner edge of the narrow diameter portion 52. The carrier projection 49 can be engaged. In the present embodiment, the internal gear protrusion 54 corresponds to the third member engaging portion in the present invention.

＜遊星歯車部材６０＞
遊星歯車部材６０は、遊星歯車機構Ｓを構成する部材であり、外周面にギア歯を有している。本実施形態において、遊星歯車部材６０は４つ設けられる。各遊星歯車部材６０は、その貫通孔６２に後キャリア部材４２の遊星歯車保持軸４８が通され、遊星歯車保持軸４８に回転可能に保持される。そして、遊星歯車部材６０は、太陽歯車部材３０の太陽ギア部３２及び内歯車部材５０の内歯部５３と歯合するようになっている。 <Planetary gear member 60>
The planetary gear member 60 is a member constituting the planetary gear mechanism S, and has gear teeth on the outer peripheral surface. In the present embodiment, four planetary gear members 60 are provided. Each planetary gear member 60 is passed through the through-hole 62 and the planetary gear holding shaft 48 of the rear carrier member 42 is passed through, and is rotatably held by the planetary gear holding shaft 48. The planetary gear member 60 meshes with the sun gear portion 32 of the sun gear member 30 and the internal gear portion 53 of the internal gear member 50.

＜コイルスプリング７０・カラー８０＞
コイルスプリング７０及びカラー８０は、後ケース２２に対する内歯車部材５０の相対回転の許容及び規制を切り替える回転規制部材として用いられる。コイルスプリング７０は、円筒状に巻回された金属線の両端がそれぞれ径方向内側に突出するコイルスプリング突起７１となっている。コイルスプリング７０は、図５に示すように、後キャリア部材４２の後円筒部４７の外周に、一対のコイルスプリング突起７１が内歯車突起５４を挟むよう配置される。コイルスプリング７０は、内歯車突起５４が回転すると拡径するようになっている。 <Coil spring 70, collar 80>
The coil spring 70 and the collar 80 are used as a rotation restricting member that switches permission and restriction of relative rotation of the internal gear member 50 with respect to the rear case 22. The coil spring 70 is a coil spring protrusion 71 in which both ends of a metal wire wound in a cylindrical shape protrude radially inward. As shown in FIG. 5, the coil spring 70 is disposed on the outer periphery of the rear cylindrical portion 47 of the rear carrier member 42 so that a pair of coil spring protrusions 71 sandwich the internal gear protrusion 54. The coil spring 70 expands in diameter when the internal gear projection 54 rotates.

カラー８０は、金属製の薄肉リング状の部材である。カラー８０は、後端の円周方向の対向２ヶ所に係合溝８１を備えており、当該係合溝８１が後ケース２２の突起２７ｃと係合することで後ケース２２に対して固定され、回転不能となっている。また、カラー８０の内側にはコイルスプリング７０が配置され、カラー８０の内径はコイルスプリング７０の外径よりも僅かに大きな径となっている。このような構成により、コイルスプリング７０は、縮径した際にはカラー８０（すなわち、ケース部材２０）に対して相対回転可能となり、拡径した際にはカラー８０に対して相対回転不能となるようになっている。   The collar 80 is a metal thin-walled ring-shaped member. The collar 80 includes engagement grooves 81 at two positions in the circumferential direction at the rear end, and the engagement grooves 81 are fixed to the rear case 22 by engaging with the protrusions 27 c of the rear case 22. It is impossible to rotate. A coil spring 70 is disposed inside the collar 80, and the inner diameter of the collar 80 is slightly larger than the outer diameter of the coil spring 70. With this configuration, the coil spring 70 can rotate relative to the collar 80 (that is, the case member 20) when the diameter is reduced, and cannot rotate relative to the collar 80 when the diameter is increased. It is like that.

（２）動作の説明
（２−１）駆動力伝達装置１０の動作
次に、上記のような構成の駆動力伝達装置１０の動作について、図８のタイミングチャート及び、図４のＢ−Ｂ断面における各部材の動作を示す図９Ａ〜図９Ｄの説明図を用いて説明する。 (2) Description of Operation (2-1) Operation of Driving Force Transmission Device 10 Next, regarding the operation of the driving force transmission device 10 configured as described above, the timing chart of FIG. 8 and the BB cross section of FIG. 9A to 9D illustrating the operation of each member in FIG.

＜局面（ｉ）＞
まず、初期状態において、各部材は図９Ａに示す位置関係にある、すなわち、キャリア４０のキャリア突起４９が、反時計回りに回転するとすぐにコイルスプリング突起７１と当接する位置にあるとする。この状態で入力軸９の回転と連動して太陽歯車部材３０が時計回りの回転（ＣＷ回転）を開始すると、図６において、太陽歯車部材３０と歯合する４つの遊星歯車部材６０がそれぞれ遊星歯車保持軸４８を中心に反時計回りに回転（ＣＣＷ回転）する。すると、遊星歯車部材６０を保持するキャリア４０は時計回りに回転しようとし、遊星歯車部材６０と歯合する内歯車部材５０は反時計回りに回転しようとする。すなわち、図９Ａにおいて、キャリア突起４９が時計回りに回転しようとし、内歯車突起５４が反時計回りに回転しようとする。 <Aspect (i)>
First, in the initial state, it is assumed that the members are in the positional relationship shown in FIG. 9A, that is, the carrier protrusion 49 of the carrier 40 is in a position where it abuts on the coil spring protrusion 71 as soon as it rotates counterclockwise. When the sun gear member 30 starts to rotate clockwise (CW rotation) in conjunction with the rotation of the input shaft 9 in this state, the four planetary gear members 60 that mesh with the sun gear member 30 in FIG. It rotates counterclockwise about the gear holding shaft 48 (CCW rotation). Then, the carrier 40 holding the planetary gear member 60 tries to rotate clockwise, and the internal gear member 50 that meshes with the planetary gear member 60 tries to rotate counterclockwise. That is, in FIG. 9A, the carrier protrusion 49 attempts to rotate clockwise, and the internal gear protrusion 54 attempts to rotate counterclockwise.

＜局面（ｉ）〜局面（ｉｉ）＞
ここで、キャリア４０は昇降軸１１に接続され、昇降軸１１に接続された巻取コーン６、昇降コード５及びボトムレール４がキャリア４０に対する回転抵抗となっているため、まずは内歯車部材５０の反時計回りが開始される。ところが、内歯車部材５０は、僅かに回転したところで内歯車突起５４がコイルスプリング突起７１に当接して押圧し、コイルスプリング７０が拡径して回転不能となる（回転抵抗が増大し、回転が規制された状態）。したがって、内歯車部材５０は僅かなクリアランス分の反時計回りの回転後、回転停止状態となる。 <Aspect (i) to Aspect (ii)>
Here, since the carrier 40 is connected to the elevating shaft 11 and the winding cone 6, the elevating cord 5 and the bottom rail 4 connected to the elevating shaft 11 are rotational resistances with respect to the carrier 40, first, the internal gear member 50 Counterclockwise starts. However, when the internal gear member 50 is slightly rotated, the internal gear protrusion 54 comes into contact with and presses against the coil spring protrusion 71, and the coil spring 70 expands in diameter and becomes unrotatable (rotational resistance increases and rotation is reduced). Regulated state). Therefore, after the internal gear member 50 rotates counterclockwise by a slight clearance, the internal gear member 50 is stopped.

その結果、遊星歯車機構Ｓにおいて、太陽歯車部材３０の時計回りの回転に対し内歯車部材５０が停止状態となるため、キャリア４０が時計回りの回転を開始する（図８及び図９Ｂ参照）。この際、太陽歯車部材３０の回転に対してキャリア４０は、（太陽ギア部３２のギア歯の数）／（太陽ギア部３２のギア歯の数＋内歯部５３のギア歯の数）の変速比で減速回転することになり、駆動力伝達装置１０は昇降軸１１に時計回りの減速回転を伝達する。この変速比が、本発明における第１の変速比である。   As a result, in the planetary gear mechanism S, since the internal gear member 50 is stopped with respect to the clockwise rotation of the sun gear member 30, the carrier 40 starts to rotate clockwise (see FIGS. 8 and 9B). At this time, the carrier 40 with respect to the rotation of the sun gear member 30 is (number of gear teeth of the sun gear portion 32) / (number of gear teeth of the sun gear portion 32 + number of gear teeth of the internal tooth portion 53). The drive force transmission device 10 transmits the clockwise reduced rotation to the lift shaft 11 at a reduced speed. This gear ratio is the first gear ratio in the present invention.

＜局面（ｉｉ）＞
キャリア４０がさらに回転を続けると、図９Ｃに示すようにキャリア突起４９がコイルスプリング突起７１に当接する。すると、コイルスプリング７０が押圧されて縮径し、カラー８０に対して回転可能な状態となる（回転抵抗が低減され、規制が解除された状態）。この時、コイルスプリング突起７１はキャリア突起４９と内歯車突起５４に挟まれた状態である。なお、初期状態から局面（ｉｉ）となるまでの太陽歯車部材３０の回転角度が本発明における所定角度である。この所定角度は、太陽ギア部３２、内歯部５３及び遊星歯車部材６０の歯数（変速比）と、キャリア突起４９及び内歯車突起５４の扇形形状の中心角によって規定することができる。 <Aspect (ii)>
As the carrier 40 continues to rotate, the carrier protrusion 49 comes into contact with the coil spring protrusion 71 as shown in FIG. 9C. Then, the coil spring 70 is pressed to reduce the diameter, and is in a state where it can rotate with respect to the collar 80 (a state where the rotational resistance is reduced and the restriction is released). At this time, the coil spring protrusion 71 is sandwiched between the carrier protrusion 49 and the internal gear protrusion 54. In addition, the rotation angle of the sun gear member 30 until it becomes a situation (ii) from an initial state is a predetermined angle in this invention. This predetermined angle can be defined by the number of teeth (transmission ratio) of the sun gear portion 32, the internal gear portion 53, and the planetary gear member 60, and the sector-shaped center angle of the carrier projection 49 and the internal gear projection 54.

＜局面（ｉｉ）〜局面（ｉｉｉ）＞
上記局面（ｉｉ）の状態でさらに太陽歯車部材３０が時計回りに回転すると、キャリア突起４９は時計回り、内歯車突起５４は反時計回りに回転しようとするため、もはやキャリア４０と内歯車部材５０はもはや相対回転ができない。その結果、太陽歯車部材３０の時計回りの回転に伴って、キャリア４０、内歯車部材５０、遊星歯車部材６０及びコイルスプリング７０がケース部材２０内で一体的に時計回りの回転を開始する（図８及び図９Ｃ〜図９Ｄ参照）。このとき、遊星歯車部材６０は自転せず、太陽歯車部材３０、キャリア４０、内歯車部材５０及び遊星歯車部材６０の相対的な位置関係は変化しない。つまり、この際、太陽歯車部材３０の回転に対してキャリア４０は、１対１の変速比、すなわち等速で回転することになり、駆動力伝達装置１０は昇降軸１１に時計回りの等速回転を伝達する。この変速比が、本発明における第２の変速比である。 <Aspect (ii) to Aspect (iii)>
When the sun gear member 30 further rotates clockwise in the state of the above aspect (ii), the carrier protrusion 49 tries to rotate clockwise and the internal gear protrusion 54 tries to rotate counterclockwise. Can no longer rotate relative. As a result, as the sun gear member 30 rotates clockwise, the carrier 40, the internal gear member 50, the planetary gear member 60, and the coil spring 70 start to rotate clockwise in the case member 20 (FIG. 8 and FIGS. 9C-9D). At this time, the planetary gear member 60 does not rotate, and the relative positional relationship among the sun gear member 30, the carrier 40, the internal gear member 50, and the planetary gear member 60 does not change. That is, at this time, the carrier 40 rotates at a gear ratio of 1: 1, that is, at a constant speed with respect to the rotation of the sun gear member 30, and the driving force transmission device 10 rotates clockwise at a constant speed. Transmits rotation. This gear ratio is the second gear ratio in the present invention.

＜局面（ｉｉｉ）＞
入力軸９の回転が停止すると、太陽歯車部材３０の回転も停止し、すべての部材が停止して、昇降軸１１の回転も停止する。 <Aspect (iii)>
When the rotation of the input shaft 9 stops, the rotation of the sun gear member 30 also stops, all the members stop, and the rotation of the elevating shaft 11 also stops.

なお、図９Ｃ又は図９Ｄの状態において入力軸９（太陽歯車部材３０）を反時計回りに回転させた場合には、上記とは逆の動作により、操作開始直後はまずキャリア４０が反時計回りに回転し、駆動力伝達装置１０は昇降軸１１に反時計回りの減速回転を伝達する。そして、キャリア突起４９がコイルスプリング突起７１に当接した後（図９Ａ参照）は各部材が一体回転することで駆動力伝達装置１０は昇降軸１１に反時計回りの等速回転を伝達する。   When the input shaft 9 (sun gear member 30) is rotated counterclockwise in the state of FIG. 9C or FIG. 9D, the carrier 40 is first rotated counterclockwise immediately after the operation is started by the reverse operation. The driving force transmission device 10 transmits a counterclockwise decelerated rotation to the lifting shaft 11. Then, after the carrier protrusion 49 comes into contact with the coil spring protrusion 71 (see FIG. 9A), the driving force transmission device 10 transmits counterclockwise constant-speed rotation to the lifting shaft 11 as the respective members rotate together.

（２−２）横型ブラインドの動作
次に、上記の駆動力伝達装置１０を備えた横型ブラインドの動作について、図１０を用いて説明する。なお、図１０Ａ〜図１０Ｄは本実施形態の横型ブラインドを図１の右側から見た側面図であり、図１０Ａ〜図１０Ｄにおいては左側が室内側となる。また、以下では、図１０Ａに示すスラット３が全閉となった状態から、スラット３が回動して図１０Ｂに示す水平状態を経て図１０Ｃに示す逆全閉状態となり、その後、図１０Ｄに示すように上昇をする際の説明を行う。スラット３を下降させつつ逆全閉状態から全閉状態とするには、以下の動作を逆に行えば良い。 (2-2) Operation of Horizontal Blind Next, the operation of the horizontal blind provided with the driving force transmission device 10 will be described with reference to FIG. 10A to 10D are side views of the horizontal blind according to the present embodiment as viewed from the right side of FIG. 1, and in FIGS. 10A to 10D, the left side is the indoor side. In the following, from the state in which the slat 3 shown in FIG. 10A is fully closed, the slat 3 rotates to go through the horizontal state shown in FIG. 10B to the reverse fully closed state shown in FIG. 10C. As will be described, the explanation will be made when the ascending. In order to change from the reverse fully closed state to the fully closed state while lowering the slat 3, the following operation may be performed in reverse.

＜スラット３の上昇及び回動＞
スラット３が全閉状態である時（図１０Ａ参照）に、操作コード８をスラット３の上昇方向に操作すると、入力軸９が回転を開始する。このとき、駆動力伝達装置１０は図９Ａに示す上記局面（ｉ）の状態となっており、駆動力伝達装置１０によって昇降軸１１は減速回転を開始する。すると、昇降軸１１の減速回転により、巻取コーン６が回転して昇降コード５がヘッドボックス１内に引き込まれ、スラット３が上昇を開始する。同時に、角度調整機構１２のチルトドラム（図示せず）が回転して、スラット３が回動動作を開始する。なお、図１０Ｂはスラット３の回動の途中を示す図であり、このとき、駆動力伝達装置１０は図９Ｂに示すように、キャリア４０のみが回転する状態である（局面（ｉ）〜（ｉｉ）参照）。また、スラット３回動時にスラット３が上昇しないよう、昇降コード５にたるみを持たせる構成とすることも可能である。 <Raising and turning of slat 3>
When the operation cord 8 is operated in the upward direction of the slat 3 when the slat 3 is in the fully closed state (see FIG. 10A), the input shaft 9 starts to rotate. At this time, the driving force transmission device 10 is in the state of the above-described aspect (i) shown in FIG. 9A, and the elevating shaft 11 starts decelerating rotation by the driving force transmission device 10. Then, the take-up cone 6 is rotated by the decelerating rotation of the elevating shaft 11, the elevating cord 5 is drawn into the head box 1, and the slat 3 starts to rise. At the same time, the tilt drum (not shown) of the angle adjustment mechanism 12 rotates, and the slat 3 starts to rotate. FIG. 10B is a diagram showing the middle of rotation of the slat 3, and at this time, as shown in FIG. 9B, the driving force transmission device 10 is in a state where only the carrier 40 rotates (phases (i) to ( see ii)). Moreover, it is also possible to make the lifting / lowering cord 5 have a slack so that the slat 3 does not rise when the slat 3 rotates.

＜スラット３の回動停止＞
さらに操作コード８の操作を続けると、スラット３は図１０Ｃの逆全閉状態となり、これと略同一のタイミングで駆動力伝達装置１０のキャリア突起４９が図９Ｃに示すように、キャリア突起４９がコイルスプリング突起７１と当接する状態となる（局面（ｉｉ）参照）。 <Rotation stop of slat 3>
When the operation cord 8 is further operated, the slat 3 is in the reverse fully closed state shown in FIG. 10C. At substantially the same timing as this, the carrier protrusion 49 of the driving force transmission device 10 is moved as shown in FIG. It will be in the state contact | abutted with the coil spring protrusion 71 (refer aspect (ii)).

＜スラット３の上昇＞
その後さらに操作コード８の操作を続けると、駆動力伝達装置１０によって昇降軸１１は入力軸９と等速の回転を開始し、スラット３はそれまでよりも速い速度で上昇するようになる（図９Ｃ参照）。この時には、太陽歯車部材３０、キャリア４０、内歯車部材５０、遊星歯車部材６０及びコイルスプリング７０は一体回転している（図９Ｄ参照）。 <Rise of slat 3>
If the operation of the operation cord 8 is continued thereafter, the lifting shaft 11 starts rotating at the same speed as the input shaft 9 by the driving force transmission device 10, and the slat 3 rises at a higher speed than before (FIG. 9C). At this time, the sun gear member 30, the carrier 40, the internal gear member 50, the planetary gear member 60, and the coil spring 70 are integrally rotated (see FIG. 9D).

＜スラット３の停止＞
最後に、操作コード８の操作を停止して入力軸９を停止させると、昇降軸１１の回転も停止し、スラット３の上昇が停止する。 <Stop of slat 3>
Finally, when the operation of the operation cord 8 is stopped and the input shaft 9 is stopped, the rotation of the elevating shaft 11 is also stopped and the raising of the slat 3 is stopped.

なお、上記駆動力伝達装置１０に用いられる遊星歯車機構Ｓは、太陽歯車部材３０、キャリア４０、内歯車部材５０及び遊星歯車部材６０の４つの部材から構成されるが、このうち遊星歯車部材６０を除く３つの部材は、どの部材に回転を入力し、どの部材から回転を出力するかを任意に設定することができる。上記実施形態では入力軸９と接続する部材を太陽歯車部材３０、昇降軸１１（出力軸）と接続する部材をキャリア４０、回転規制部材であるコイルスプリング７０及びカラー８０により回転の規制と許容を切り替える部材を内歯車部材５０とすることで、複数の変速比の回転を出力できるようにしていたが、これら３つの役割は任意である。つまり、図１１に示すように、入力軸と接続する部材、昇降軸と接続する部材及び、回転規制部材により回転の規制と許容が切り替えられる部材を任意に入れ替えることが可能である。   The planetary gear mechanism S used in the driving force transmission device 10 is composed of four members: a sun gear member 30, a carrier 40, an internal gear member 50, and a planetary gear member 60. Of these, the planetary gear member 60 is included. The three members except for can be arbitrarily set as to which member the rotation is input and from which the rotation is output. In the above embodiment, the member that is connected to the input shaft 9 is the sun gear member 30, the member that is connected to the lifting shaft 11 (output shaft) is the carrier 40, the coil spring 70 that is the rotation restricting member, and the collar 80, so that the rotation is regulated and allowed. Although the member to be switched is the internal gear member 50 so that rotation of a plurality of gear ratios can be output, these three roles are arbitrary. That is, as shown in FIG. 11, it is possible to arbitrarily replace the member connected to the input shaft, the member connected to the lifting shaft, and the member whose rotation is restricted and permitted by the rotation restricting member.

これらの組み合わせは、回転開始直後の変速比と一定回転後の変速比をどのように設定するかにより選択することが好ましい。上記実施形態のように、駆動力伝達装置１０を１つの操作コードの操作により開閉及び角度調節可能とした昇降装置に用いる場合には、操作コード８の操作開始直後はスラット３の角度を調整するため入力回転を減速して出力し、スラット３の回動終了後は減速せずに出力することが好ましいため、上記実施形態の組み合わせを選択している。   These combinations are preferably selected depending on how to set the gear ratio immediately after the start of rotation and the gear ratio after constant rotation. When the driving force transmission device 10 is used in a lifting device that can be opened and closed and adjusted in angle by operating one operation cord as in the above embodiment, the angle of the slat 3 is adjusted immediately after the operation of the operation cord 8 is started. Therefore, since the input rotation is decelerated and output, and it is preferable to output without decelerating after the end of the rotation of the slat 3, the combination of the above embodiments is selected.

（３）作用効果
上記のような駆動力伝達装置１０及び横型ブラインドでは、次に示す作用効果を得ることができる。
（イ）遊星歯車機構Ｓの太陽歯車部材３０を入力軸９と接続し、キャリア４０を昇降軸１１（出力軸）と接続し、内歯車部材５０の回転の許容と規制を回転規制部材であるコイルスプリング７０及びカラー８０により切り替えることによって、駆動力伝達装置１０は、同一の入力回転に対し、複数の変速比の回転を出力することが可能となる。特に、入力回転の開始直後は減速回転を出力し、一定回転後は等速回転を出力することが可能となる。
（ロ）キャリア突起４９、内歯車突起５４がコイルスプリング突起７１に対して逆方向に作用することによってコイルスプリング７０が縮径、拡径してキャリア４０の回転の規制と許容が切り替わる構成であり、略同心円上にキャリア突起４９、内歯車突起５４及びコイルスプリング突起７１を配置することで、駆動力伝達装置１０の軸方向（前後方向）のスペースを軽減することが可能となる。
（ハ）遊星歯車機構Ｓの太陽歯車部材３０、キャリア４０及び内歯車部材５０の役割を図１１に示す組み合わせから適切に選択することで、初動（入力回転開始）において減速させることも増速させることも可能である。
（ニ）遊星歯車機構Ｓの太陽歯車部材３０に回転を入力し、キャリア４０から回転を出力させることで、同軸での変速が可能である。
（ホ）遊星歯車機構Ｓのいずれか１つに回転を入力し、他の１つから回転を出力する構成であることから、変速が切り替わる際に遊び（空転）が生じない。
（ヘ）横型ブラインドに上記構成の駆動力伝達装置１０を用いることで、スラット３の昇降動作における初動において各スラット３を回動させるときには、昇降軸１１に減速回転を出力することでラダーコード２の移動に対して確実にスラット３を回動させ、スラット３の回動終了後には、等速回転を出力して効率的にスラット３を昇降させることが可能である。 (3) Operational effects In the driving force transmission device 10 and the horizontal blind as described above, the following operational effects can be obtained.
(A) The sun gear member 30 of the planetary gear mechanism S is connected to the input shaft 9, the carrier 40 is connected to the lifting shaft 11 (output shaft), and the rotation permission and restriction of the internal gear member 50 are rotation restriction members. By switching between the coil spring 70 and the collar 80, the driving force transmission device 10 can output a plurality of gear ratio rotations for the same input rotation. In particular, it is possible to output a reduced speed rotation immediately after the start of the input rotation, and to output a constant speed rotation after a fixed rotation.
(B) The carrier protrusion 49 and the internal gear protrusion 54 act in the opposite direction with respect to the coil spring protrusion 71, whereby the coil spring 70 is reduced in diameter and expanded to restrict the restriction and allowance of the rotation of the carrier 40. By arranging the carrier projection 49, the internal gear projection 54, and the coil spring projection 71 on substantially concentric circles, it is possible to reduce the space in the axial direction (front-rear direction) of the driving force transmission device 10.
(C) By appropriately selecting the roles of the sun gear member 30, the carrier 40 and the internal gear member 50 of the planetary gear mechanism S from the combinations shown in FIG. It is also possible.
(D) By inputting the rotation to the sun gear member 30 of the planetary gear mechanism S and outputting the rotation from the carrier 40, a coaxial shift can be achieved.
(E) Since the rotation is input to any one of the planetary gear mechanisms S and the rotation is output from the other one, no play (idling) occurs when the shift is switched.
(F) By using the driving force transmission device 10 configured as described above for the horizontal blind, when the slats 3 are rotated in the initial movement of the slats 3 in the up-and-down motion, the ladder code 2 is output by outputting a reduced rotation to the up-and-down shaft 11. The slat 3 can be reliably rotated with respect to the movement of the slat 3, and after the slat 3 has finished rotating, the slat 3 can be efficiently moved up and down by outputting a constant speed rotation.

なお、本発明は、以下の態様でも実施可能である。
・上述した実施形態は駆動力伝達装置１０を横型ブラインドに適用したものであったが、横型ブラインド以外の遮蔽装置、例えば、縦型ブラインド等に適用することも可能である。
・上記実施形態においては、回転規制部材としてのコイルスプリング７０がカラー８０の内周面に配置され、コイルスプリング７０が拡径することで回転不能となり、縮径することで回転可能となる構成であったが、回転規制部材として、コイルスプリング７０をカラー８０の外周面に配置し、コイルスプリング７０が縮径することで回転不能となり、拡径することで回転可能となる構成のものを用いることも可能である。 In addition, this invention can be implemented also with the following aspects.
-Although embodiment mentioned above applied the driving force transmission apparatus 10 to the horizontal blind, it is also possible to apply to shielding apparatuses other than a horizontal blind, for example, a vertical blind.
In the above embodiment, the coil spring 70 as the rotation restricting member is disposed on the inner peripheral surface of the collar 80, and the coil spring 70 becomes non-rotatable by expanding the diameter, and can be rotated by reducing the diameter. However, as the rotation restricting member, the coil spring 70 is arranged on the outer peripheral surface of the collar 80, and the rotation of the coil spring 70 becomes impossible when the diameter is reduced, and the rotation becomes possible when the diameter is increased. Is also possible.

１ ：ヘッドボックス
２ ：ラダーコード
３ ：スラット
４ ：ボトムレール
５ ：昇降コード（開閉コード）
６ ：巻取コーン
７ ：昇降装置
８ ：操作コード（操作部）
９ ：入力軸
１０ ：駆動力伝達装置
１１ ：昇降軸（巻取軸）
１２ ：角度調整機構
２０ ：ケース部材
２１ ：前ケース
２１ａ ：貫通孔
２２ ：後ケース
２３ ：板状部
２４ａ ：係合突起
２４ｂ ：係合突起
２５ ：底壁部
２５ａ ：貫通孔
２６ ：側壁部
２７ ：収容空間
２７ａ ：大収容空間
２７ｂ ：小収容空間
２７ｃ ：突起
２８ａ ：係合溝
２８ｂ ：係合溝
３０ ：太陽歯車部材（第１部材）
３１ ：入力側接続部
３２ ：太陽ギア部
３３ ：円筒部
４０ ：キャリア（第２部材）
４１ ：前キャリア部材
４１ａ ：貫通孔
４２ ：後キャリア部材
４３ ：前円筒部
４４ ：円盤部
４４ａ ：嵌合孔
４５ ：支持柱
４５ａ ：突起
４６ ：円盤部
４６ａ ：嵌合孔
４６ｂ ：保持部
４７ ：後円筒部
４７ａ ：出力側接続部
４８ ：遊星歯車保持軸
４８ａ ：突起
４９ ：キャリア突起（第２部材係合部）
５０ ：内歯車部材（第３部材）
５１ ：薄肉筒状部
５２ ：狭径部
５３ ：内歯部
５４ ：内歯車突起（第３部材係合部）
６０ ：遊星歯車部材
６２ ：貫通孔
７０ ：コイルスプリング（回転規制部材）
７１ ：コイルスプリング突起
８０ ：カラー（回転規制部材）
８１ ：係合溝
Ｓ ：遊星歯車機構 1: Head box 2: Ladder cord 3: Slat 4: Bottom rail 5: Lifting cord (opening / closing cord)
6: Winding cone 7: Lifting device 8: Operation cord (operation unit)
9: Input shaft 10: Driving force transmission device 11: Lifting shaft (winding shaft)
12: Angle adjusting mechanism 20: Case member 21: Front case 21a: Through hole 22: Rear case 23: Plate-like part 24a: Engaging protrusion 24b: Engaging protrusion 25: Bottom wall part 25a: Through hole 26: Side wall part 27 : Accommodation space 27a: large accommodation space 27b: small accommodation space 27c: projection 28a: engagement groove 28b: engagement groove 30: sun gear member (first member)
31: Input side connection part 32: Sun gear part 33: Cylindrical part 40: Carrier (second member)
41: Front carrier member 41a: Through hole 42: Rear carrier member 43: Front cylindrical portion 44: Disc portion 44a: Fitting hole 45: Supporting column 45a: Protrusion 46: Disc portion 46a: Fitting hole 46b: Holding portion 47: Rear cylindrical portion 47a: output side connection portion 48: planetary gear holding shaft 48a: protrusion 49: carrier protrusion (second member engaging portion)
50: Internal gear member (third member)
51: Thin cylindrical portion 52: Narrow diameter portion 53: Internal tooth portion 54: Internal gear projection (third member engaging portion)
60: Planetary gear member 62: Through hole 70: Coil spring (rotation restricting member)
71: Coil spring protrusion 80: Collar (rotation restricting member)
81: engagement groove S: planetary gear mechanism

Claims (10)

第１部材と、第２部材と、第３部材とを備え、前記第１部材への入力回転を前記第２部材の回転として出力する駆動力伝達装置であって、
前記第１部材の回転に伴って前記第２部材と前記第３部材の少なくとも一方が回転するよう構成されており、
前記第３部材の回転の規制と許容とを切り替える回転規制部材を備える、駆動力伝達装置。 A driving force transmission device comprising a first member, a second member, and a third member, and outputting an input rotation to the first member as a rotation of the second member,
It is configured such that at least one of the second member and the third member rotates with the rotation of the first member,
A driving force transmission device comprising a rotation restriction member that switches between restriction and allowance of rotation of the third member. 前記回転規制部材が前記第３部材の回転の規制と許容とを切り替えることで、前記第２部材の出力する回転の変速比が切り替わるよう構成される、請求項１に記載の駆動力伝達装置。   The driving force transmission device according to claim 1, wherein the rotation restriction member is configured to switch a rotation speed ratio output from the second member by switching between restriction and allowance of rotation of the third member. 前記回転規制部材は、前記第３部材に与える回転抵抗を変化させることで、前記第３部材の回転の規制と許容とを切り替えるよう構成される、請求項２に記載の駆動力伝達装置。   The driving force transmission device according to claim 2, wherein the rotation restricting member is configured to switch between restricting and allowing rotation of the third member by changing a rotation resistance applied to the third member. 前記回転規制部材は、前記第３部材の回転に伴って回転抵抗が増大することで前記第３部材の回転を規制し、前記第２部材の回転に伴って前記回転抵抗が低減されることで前記第３部材の回転を許容するよう構成される、請求項３に記載の駆動力伝達装置。   The rotation restricting member restricts the rotation of the third member by increasing the rotation resistance with the rotation of the third member, and reduces the rotation resistance with the rotation of the second member. The driving force transmission device according to claim 3, wherein the driving force transmission device is configured to allow rotation of the third member. 前記第１部材が回転開始後所定角度回転するまでは、前記回転規制部材が前記第３部材の回転を規制するとともに前記第２部材が第１の変速比で回転を出力し、
前記第１部材が前記所定角度回転した後は、前記回転規制部材が前記第３部材の回転の規制を解除するとともに前記第１部材、前記第２部材及び前記第３部材が一体回転して、前記第２部材が第２の変速比で回転を出力するよう構成される、請求項４に記載の駆動力伝達装置。 The rotation restricting member restricts the rotation of the third member and the second member outputs the rotation at the first gear ratio until the first member rotates by a predetermined angle after the rotation starts.
After the first member rotates by the predetermined angle, the rotation restricting member releases the restriction of the rotation of the third member, and the first member, the second member, and the third member rotate integrally, The driving force transmission device according to claim 4, wherein the second member is configured to output rotation at a second speed ratio. 前記第２部材は円周方向の一部の位置に第２部材係合部を備え、前記第３部材は、円周方向の一部の位置に第３部材係合部を備えており、
前記第２部材係合部と前記第３部材係合部が前記回転規制部材に対して逆方向に作用することによって前記第３部材の回転の規制と許容が切り替わるよう構成される、請求項４又は請求項５に記載の駆動力伝達装置。 The second member includes a second member engaging portion at a partial position in the circumferential direction, and the third member includes a third member engaging portion at a partial position in the circumferential direction;
The rotation restriction and tolerance of the third member are switched by the second member engagement portion and the third member engagement portion acting in a reverse direction with respect to the rotation restriction member. Or the driving force transmission apparatus of Claim 5. 前記第１部材、前記第２部材、前記第３部材及び前記回転規制部材を収容するケース部材と、前記ケース部材に固定された円筒状のカラーとを備え、
前記回転規制部材は、前記カラーの外周面又は内周面に配置され且つ径方向に延びる突起を有するコイルスプリングを備えており、
前記第３部材係合部は、前記第３部材の回転により前記コイルスプリングが縮径又は拡径して前記カラーに対して相対回転不能となるよう前記突起を押圧する位置に配置され、
前記第２部材係合部は、前記第２部材の回転により前記コイルスプリングが前記カラーに対して相対回転可能となるよう前記突起を押圧する位置に配置される、請求項６に記載の駆動力伝達装置。 A case member that houses the first member, the second member, the third member, and the rotation regulating member; and a cylindrical collar fixed to the case member;
The rotation restricting member includes a coil spring disposed on the outer peripheral surface or the inner peripheral surface of the collar and having a protrusion extending in the radial direction,
The third member engaging portion is disposed at a position that presses the protrusion so that the coil spring is contracted or expanded by rotation of the third member so that relative rotation with respect to the collar becomes impossible.
The driving force according to claim 6, wherein the second member engaging portion is disposed at a position that presses the protrusion so that the coil spring can rotate relative to the collar by the rotation of the second member. Transmission device. 遊星歯車機構を備え、前記第１部材、前記第２部材及び前記第３部材は、前記遊星歯車機構の太陽歯車部材、キャリア及び内歯車部材によって構成される、請求項１〜請求項７のいずれかに記載の駆動力伝達装置。   The planetary gear mechanism is provided, and the first member, the second member, and the third member are configured by a sun gear member, a carrier, and an internal gear member of the planetary gear mechanism. A driving force transmission device according to claim 1. 前記第１部材を前記太陽歯車部材とし、前記第２部材を前記キャリアとし、前記第３部材を前記内歯車部材とする、請求項８に記載の駆動力伝達装置。   The driving force transmission device according to claim 8, wherein the first member is the sun gear member, the second member is the carrier, and the third member is the internal gear member. 遮蔽部材と、前記遮蔽部材を開閉させる開閉コードと、操作部の操作により回転する入力軸と、入力軸の回転に伴って回転して前記開閉コードの巻取り及び巻戻しを行う巻取軸とを備え、前記巻取軸の回転と連動して前記遮蔽部材の角度を変更可能に構成された遮蔽装置であって、
請求項１〜請求項９のいずれかに記載の前記駆動力伝達装置を備え、
前記駆動力伝達装置は、前記入力軸の回転を前記巻取軸に伝達するよう構成される、遮蔽装置。 A shielding member, an opening / closing cord for opening and closing the shielding member, an input shaft that rotates by operation of an operation unit, and a winding shaft that rotates along with the rotation of the input shaft to wind and unwind the opening / closing cord. A shielding device configured to change the angle of the shielding member in conjunction with the rotation of the winding shaft,
The driving force transmission device according to any one of claims 1 to 9,
The driving force transmission device is a shielding device configured to transmit rotation of the input shaft to the winding shaft.
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Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS563994U (en) * 1979-06-22 1981-01-14
US20060108076A1 (en) * 2004-11-19 2006-05-25 Shien-Te Huang Rotor brake mechanism for curtain linkage system
JP2008088626A (en) * 2006-09-29 2008-04-17 Nichibei Co Ltd Elevating apparatus for blind
JP2017066675A (en) * 2015-09-29 2017-04-06 立川ブラインド工業株式会社 Driving force transmission device of solar shading device

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS563994U (en) * 1979-06-22 1981-01-14
US20060108076A1 (en) * 2004-11-19 2006-05-25 Shien-Te Huang Rotor brake mechanism for curtain linkage system
JP2008088626A (en) * 2006-09-29 2008-04-17 Nichibei Co Ltd Elevating apparatus for blind
JP2017066675A (en) * 2015-09-29 2017-04-06 立川ブラインド工業株式会社 Driving force transmission device of solar shading device

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