JPH0817734B2 - Drive mechanism - Google Patents
Drive mechanismInfo
- Publication number
- JPH0817734B2 JPH0817734B2 JP22002387A JP22002387A JPH0817734B2 JP H0817734 B2 JPH0817734 B2 JP H0817734B2 JP 22002387 A JP22002387 A JP 22002387A JP 22002387 A JP22002387 A JP 22002387A JP H0817734 B2 JPH0817734 B2 JP H0817734B2
- Authority
- JP
- Japan
- Prior art keywords
- movable body
- spline
- shaft portion
- carrier
- planetary gear
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired - Fee Related
Links
Landscapes
- Curtains And Furnishings For Windows Or Doors (AREA)
- One-Way And Automatic Clutches, And Combinations Of Different Clutches (AREA)
Description
【発明の詳細な説明】 （イ）発明の分野 この発明は、例えば、カーテンを開閉する駆動機構で
あって、さらに詳しくは、左右に配置されたカーテンを
相反する方向に開閉駆動する駆動機構に使用することが
できるような駆動機構に関する。Description: (a) Field of the Invention The present invention relates to, for example, a drive mechanism that opens and closes a curtain, and more specifically, to a drive mechanism that opens and closes curtains disposed on the left and right in opposite directions. A drive mechanism that can be used.
（ロ）発明の背景 当出願人は、カーテンの開閉駆動装置（特願昭60−25
913号）を既に開発している。(B) Background of the Invention The applicant of the present invention has proposed a curtain opening / closing drive device (Japanese Patent Application No. 60-25).
913) has already been developed.
この駆動装置はカーテンを手動で開閉できるように、
駆動系に介設した遊星歯車機構のインターナルギャを回
動自在に支持し、電動力で駆動するときは、上述のイン
ターナルギャを電磁クラッチのONでロックし、通常は電
磁クラッチがOFFであることで、インターナルギャがフ
リーとなり、カーテンを手動で開閉すると、その回動力
は、インターナルギャを遊転させることで手動操作によ
る開閉を可能にした構成の装置である。This drive allows you to open and close the curtain manually,
When the internal gear of the planetary gear mechanism provided in the drive system is rotatably supported and is driven by electric power, the internal gear described above is locked by turning on the electromagnetic clutch, and normally the electromagnetic clutch is off. As a result, the internal gear becomes free, and when the curtain is manually opened / closed, the turning power of the internal gear allows the internal gear to idle and open / close manually.
しかし、このように構成した場合、電磁クラッチが必
要となることで、高価となり、装置も嵩高くなる問題点
を有する。However, in the case of such a configuration, since the electromagnetic clutch is required, there is a problem that the cost becomes high and the apparatus becomes bulky.
（ハ）発明の目的 この発明は、上述のようなカーテンの開閉駆動機構に
使用するばかりでなく、他の駆動機構として広く使用可
能であり、さらに、有効なメカニカルクラッチ機構を使
用することで、安価でコンパクトな構造で負荷側の手動
操作が可能な駆動機構の提供を目的とする。(C) Object of the Invention The present invention is not only used for the curtain opening / closing drive mechanism as described above but also widely usable as another drive mechanism, and further, by using an effective mechanical clutch mechanism, It is an object of the present invention to provide a drive mechanism that is inexpensive and compact and that can be manually operated on the load side.
（ニ）発明の構成 この発明は、サンギャを入力部とする遊星歯車機構の
キャリアに出力部とする軸部を連設し、上記遊星歯車機
構のインターナルギャの上記軸部側の側面に付勢状態で
対向して、可動体を接離摺動のみ可能に対設すると共
に、相互の対向面に該可動体を接離移動させるカム面を
形成し、上記可動体の中心部には、前記軸部を挿通し、
外周面にスプラインを刻設したスプライン筒軸部を、相
対回動のみ自在にして連結し、上記可動体と前記キャリ
アとの対向面の相互には、前記カム面による移動量より
係合量が少ない係合面を形成し、前記スプライン筒軸部
の移動側には、出力軸を対設し、この出力軸の対向軸端
には前記カム面の移動量で前記スプライン筒軸部のスプ
ラインと嵌合・非嵌合されるスプラインを形成した駆動
機構であることを特徴とする。(D) Configuration of the Invention According to the present invention, a shaft portion having an output portion is connected to a carrier of a planetary gear mechanism having a sun gear as an input portion, and is attached to a side surface on the shaft portion side of an internal gear of the planetary gear mechanism. The movable bodies are opposed to each other in a biased state so as to be capable of only contacting and separating sliding, and cam surfaces for moving the movable bodies toward and away from each other are formed on mutually opposing surfaces. Insert the shaft,
A spline cylinder shaft portion having a spline engraved on the outer peripheral surface is connected so as to be rotatable only relative to each other, and the opposing surface of the movable body and the carrier has an engagement amount larger than the movement amount by the cam surface. A small number of engagement surfaces are formed, and an output shaft is provided on the moving side of the spline cylinder shaft portion, and the output shaft is opposed to the spline of the spline cylinder shaft portion by the movement amount of the cam surface at the opposite shaft end. It is characterized in that the drive mechanism is formed with a spline that is fitted or not fitted.
（ホ）発明の作用 この発明の駆動機構は、遊星歯車機構のサンギャに駆
動力が入力されると、キャリアは可動体との間で、係合
面の係合によって、非回動状態におかれているので、イ
ンターナルギャが回動する。(E) Action of the Invention In the drive mechanism of the present invention, when the drive force is input to the sun gear of the planetary gear mechanism, the carrier is brought into the non-rotating state by the engagement of the engagement surface with the movable body. Since it has been done, the internal gear rotates.
この回動力はカム面を介し可動体を付勢力に抗して後
退することになり、この後退で可動体のスプライン筒軸
部と、出力軸のスプラインとが嵌合し、出力軸に駆動力
が出力し得る状態となる。This turning force causes the movable body to retreat against the urging force via the cam surface, and by this retreat, the spline cylinder shaft portion of the movable body and the spline of the output shaft are fitted, and the driving force is applied to the output shaft. Is ready to be output.
さらに、可動体の後退でキャリアとの間の係合面の係
合が解かれると、インターナルギャの回動は停止、キャ
リアが回動することで、このキャリアの回動が可動体の
スプライン筒軸部を介して出力軸に伝達されて出力され
る。Further, when the engagement surface is disengaged from the carrier due to the retraction of the movable body, the rotation of the internal gear stops, and the rotation of the carrier causes the rotation of the carrier to be splined. The output is transmitted to the output shaft via the cylindrical shaft portion.
さらに、遊星歯車機構に駆動力が入力されていない場
合は、可動体のスプライン筒軸部は付勢力で出力軸のス
プラインと非嵌合状態にあるため、出力軸はフリーとな
り、負荷側は手動で自由に操作できる。Furthermore, when the driving force is not input to the planetary gear mechanism, the spline cylinder shaft of the movable body is not engaged with the spline of the output shaft due to the urging force, so the output shaft becomes free and the load side is manually operated. You can operate freely with.
（ヘ）発明の効果 上述の結果、この発明によれば、先行技術のように電
磁クラッチが不要であり、また、インターナルギャ、可
動体、カム面、および係合面で形成されるメカニカルク
ラッチも構造が簡単であるため、安価に構成でき、コン
パクトに構成できる。(F) Effects of the Invention As a result of the above, according to the present invention, an electromagnetic clutch is not required as in the prior art, and a mechanical clutch formed of an internal gear, a movable body, a cam surface, and an engagement surface. Since the structure is simple, it can be constructed inexpensively and compactly.
（ト）発明の実施例 この発明の一実施例を以下図面に基づいて詳述する。(G) Embodiment of the Invention One embodiment of the present invention will be described in detail below with reference to the drawings.
図面はカーテンの駆動機構を示し、第１図において、
左右のカーテン10a,10bは、１本のカーテンレール11を
開閉方向に移動するように吊下し、各カーテン10a,10b
の先頭部には、先頭ランナ12a,12bを固定している。The drawing shows the drive mechanism of the curtain, and in FIG.
The left and right curtains 10a, 10b are hung from one curtain rail 11 so as to move in the opening / closing direction, and the curtains 10a, 10b
The head runners 12a and 12b are fixed to the head portion of the.
前述のカーテンレール11の上部には、出力プーリ13と
従動プーリ14とに張設した、エンドレス状のベルト15を
配置し、このベルト15の手前側と奥側との対称位置に、
前述の先頭ランナ12a,12bを固定している。At the upper part of the curtain rail 11 described above, an endless belt 15 stretched between the output pulley 13 and the driven pulley 14 is arranged, and at the symmetrical position between the front side and the back side of the belt 15,
The above-mentioned top runners 12a and 12b are fixed.
そして、上述の出力プーリ13が正方向、または、逆方
向に回動することで、カーテン10a、10bは同時に、閉ま
たは開方向に移動し、また閉成状態時には、相互の先頭
ランナ12a,12bが当接して、カーテン10a,10bの閉成状態
を規制する。Then, the output pulley 13 is rotated in the forward direction or the reverse direction, so that the curtains 10a and 10b are simultaneously moved in the closing or opening direction, and in the closed state, the leading runners 12a and 12b are mutually closed. Contact with each other to regulate the closed state of the curtains 10a and 10b.
前述の出力プーリ13は駆動源である正逆モータ16の駆
動によって正・逆方向に回動するが、この正逆モータ16
と出力プーリ13との間には、２段の遊星歯車機構17,18
とクラッチ機構19とを介装している。The output pulley 13 is rotated in the forward and reverse directions by the drive of the forward / reverse motor 16 which is a drive source.
Between the output pulley 13 and the output pulley 13, two-stage planetary gear mechanism 17,18
And the clutch mechanism 19 are interposed.
上述の各遊星歯車機構17,18は共に同一の機構からな
り、すなわち、サンギャ20a,20b、これに噛合するプラ
ネタリギャ21a,21b、これに噛合するインターナルギャ2
2a,22b、前述のプラネタリギャ21a,21bを支持するキャ
リア23a,23bよりなり、前段の遊星歯車機構17のサンギ
ャ20aに正逆モータ16の出力軸24を連結し、前段のキャ
リア23aを後段のサンギャ20bに連結し、後段のキャリア
23bを後述するクラッチ機構19に接続している。The planetary gear mechanisms 17 and 18 described above are both composed of the same mechanism, that is, the sun gears 20a and 20b, the planetary gears 21a and 21b that mesh with the sun gears 20a and 21b, and the internal gear 2 that meshes with the planetary gears 21a and 21b.
2a, 22b, consisting of carriers 23a, 23b supporting the planetary gears 21a, 21b described above, the output shaft 24 of the forward / reverse motor 16 is connected to the sun gear 20a of the planetary gear mechanism 17 of the preceding stage, and the carrier 23a of the preceding stage is connected to the latter stage. Carrier connected to Sanga 20b, the latter stage
23b is connected to a clutch mechanism 19 described later.
第２図に示すように、上述のクラッチ機構19は次のよ
うに構成される。As shown in FIG. 2, the clutch mechanism 19 described above is configured as follows.
すなわち、後段の遊星歯車機構18のキャリア23bの上
面側中心部には軸部25を連設し、この軸部25は可動体26
とスプライン筒軸部27に挿通し、これらはキー28によっ
て、回動を禁止した状態で、相対摺動のみ可能に形成す
る。That is, the shaft portion 25 is continuously provided at the center of the upper surface side of the carrier 23b of the planetary gear mechanism 18 in the subsequent stage, and the shaft portion 25 is movable by the movable member 26.
It is inserted through the spline cylinder shaft portion 27, and these are formed so that only relative sliding is possible with the key 28 in a state where the rotation is prohibited.
上述の可動体26と、スプライン筒軸部27とは相対回動
のみ自在に遊貫連結し、Ｅリング29によって抜止めす
る。The movable body 26 and the spline cylinder shaft portion 27 are loosely connected only for relative rotation, and are prevented from coming off by an E ring 29.
上述の可動体26は、ハウジング30の内周面に形成した
スライド溝31に、その凸部32が係合することで、回動を
禁止した状態で摺動可能に支持し、スプリング33によっ
て、インターナルギャ22b側に押圧付勢している。The movable body 26 described above is slidably supported in a state in which rotation is prohibited by the slide groove 31 formed on the inner peripheral surface of the housing 30 and the projection 32 thereof being engaged, and by the spring 33, The internal gear 22b is pressed and urged.
そして、上述のインターナルギャ22bは回動のみ自在
にハウジング30に支持している。The internal gear 22b described above is supported by the housing 30 so as to be rotatable only.
上述の可動体26と前述のインターナルギャ22bとが相
互に対向する側面には、第３図イ、ロにも示すように、
相互に係合する三角凹凸形状のカム面34a,34bを形成し
て噛合し、これらカム面34a,34bの山同士が接当すると
き、可動体26は移動し、その移動量をL1とする。As shown in FIGS. 3A and 3B, on the side surfaces where the movable body 26 and the internal gear 22b described above face each other,
Triangular concavo-convex cam surfaces 34a, 34b that engage with each other are formed and meshed, and when the peaks of these cam surfaces 34a, 34b abut, the movable body 26 moves, and the amount of movement is L1. .
上述の可動体26と前述のキャリア23bとが相互に対向
する側面には、第４図イ、ロにも示すように、相互に係
合する三角凹凸形状の係合面35a,35bを形成して係合
し、これらの係合面35a,35bの山同士が係合するとき、
キャリア23bは摺動し、摺動量をL2とすると、前述の移
動量L1との関係は、L1＞L2に設定して、L1の移動量を大
きくしている。On the side surfaces of the movable body 26 and the carrier 23b facing each other, as shown in FIGS. 4A and 4B, engagement surfaces 35a, 35b of triangular concavo-convex shape that engage with each other are formed. And the peaks of these engaging surfaces 35a, 35b are engaged with each other,
When the carrier 23b slides and the sliding amount is L2, the above-mentioned relationship with the moving amount L1 is set to L1> L2 to increase the moving amount of L1.
前述のスプライン筒軸部27の上端側外周面には、スプ
ライン36を刻設し、さらに、このスプライン筒軸部27の
上部には出力軸37を対設し、この出力軸37の下部に連設
した内筒部38にはスプライン39を刻設している。A spline 36 is engraved on the outer peripheral surface on the upper end side of the spline cylinder shaft portion 27 described above, and an output shaft 37 is provided above the spline cylinder shaft portion 27 and connected to the lower portion of the output shaft 37. A spline 39 is engraved on the provided inner cylinder portion 38.
そして、これらスプライン36,39は、前述のカム面34
a,34bの操作で、スプライン筒軸部27が、係合面35a,35b
の係合量L2だけ摺動したとき、スプライン嵌合するよう
に設定され、さらに、スプライン筒軸部27が摺動しない
ときは、両者は非嵌合状態にある。The splines 36 and 39 are connected to the cam surface 34 described above.
By operating a and 34b, the spline cylinder shaft portion 27 is moved to the engaging surfaces 35a and 35b.
When the sliding amount L2 of 1 is set, the spline fitting is set so as to be fitted, and when the spline cylinder shaft portion 27 does not slide, both are in the non-fitting state.
なお、前述の出力軸37の上端には前述の出力プーリ13
が連結される。At the upper end of the output shaft 37, the output pulley 13
Are linked.
図中、40はセッタ軸、41,41は軸受メタルである。 In the figure, 40 is a setter shaft, and 41 and 41 are bearing metals.
このように構成したカーテンの駆動機構の動作を説明
する。The operation of the curtain drive mechanism thus configured will be described.
カーテン10a,10bを開、または閉の方向に操作すると
きは、正逆モータ16を正、または逆の方向に回転制御す
る。When operating the curtains 10a, 10b in the opening or closing direction, the forward / reverse motor 16 is rotationally controlled in the forward or reverse direction.
正逆モータ16の出力は１段目の遊星歯車機構17を介し
て２段目の遊星歯車機構18に入力される。The output of the forward / reverse motor 16 is input to the second stage planetary gear mechanism 18 via the first stage planetary gear mechanism 17.
この遊星歯車機構18において、キャリア23bは係合面3
5a,35bの係合で可動体26に一体であり、また、この可動
体26はスライド溝31と凸部32との係合で回動しないの
で、前述のキャリア23bは回動ができず、その結果、イ
ンターナルギャ22bが回動する。In this planetary gear mechanism 18, the carrier 23b has an engaging surface 3
5a, 35b is integrated with the movable body 26 by the engagement, and since the movable body 26 does not rotate due to the engagement of the slide groove 31 and the convex portion 32, the aforementioned carrier 23b cannot rotate, As a result, the internal gear 22b rotates.
インターナルギャ22bが回動すると、可動体26との相
互のカム面34a,34bの噛合で、可転体26がスプリング33
に抗して押上げられ、これに連動して、スプライン筒軸
部27も上昇し、このスプライン筒軸部27のスプライン36
と出力軸37のスプライン39とが嵌合する。しかし、この
時点では駆動力の伝達はない。When the internal gear 22b pivots, the cam surfaces 34a and 34b mesh with the movable body 26, causing the rotatable body 26 to move to the spring 33.
It is pushed up against, and in conjunction with this, the spline cylinder shaft part 27 also rises, and the spline 36 of this spline cylinder shaft part 27
And the spline 39 of the output shaft 37 are fitted together. However, the driving force is not transmitted at this point.
さらに、可動体26が係合量L2分押上げられることで、
キャリア23bと可動体26の相互の係合面35a,35bの係合が
外れると、キャリア23bの回動が許容されるので、イン
ターナルギャ22bの回動が停止し、サンギャ20bの回動は
プラネタリギャ21bを介してキャリア23bを回動し、この
回動が軸部25、スプライン筒軸部27を介して出力軸37を
回動し、この回動で出力プーリ13を回動し、カーテン10
a,10bが開、または閉の方向に走行される。Furthermore, by the movable body 26 being pushed up by the engagement amount L2,
When the engagement surfaces 35a, 35b of the carrier 23b and the movable body 26 are disengaged from each other, the rotation of the carrier 23b is allowed, so that the rotation of the internal gear 22b is stopped and the rotation of the sun gear 20b is prevented. The carrier 23b is rotated through the planetary gear 21b, and this rotation rotates the output shaft 37 through the shaft portion 25 and the spline cylinder shaft portion 27, and this rotation causes the output pulley 13 to rotate and the curtain. Ten
The a and 10b are driven in the open or closed direction.
次に正逆モータ16が回動を停止すると、スプリング33
によって可動体26は元の位置に復帰されるので、スプラ
イン筒軸部27が押下げられ出力軸37と、スプライン筒軸
部27の相互のスプライン36,39が外れて、動力の伝達が
断たれ、カーテン10a,10bの走行は停止する。Next, when the forward / reverse motor 16 stops rotating, the spring 33
Since the movable body 26 is returned to the original position by the spline cylinder shaft portion 27, the output shaft 37 and the splines 36 and 39 of the spline cylinder shaft portion 27 are disengaged from each other, and the power transmission is cut off. The traveling of the curtains 10a and 10b is stopped.
この状態では出力軸37がフリーとなっているので、カ
ーテン10a,10bを手動で回動することができる。In this state, since the output shaft 37 is free, the curtains 10a and 10b can be manually rotated.
このように構成することによって、回動機構は先行技
術のように電磁クラッチが不要であり、また、クラッチ
機構19（メカニカルクラッチ）も構造が簡単であるた
め、安価に構成でき、コンパクトに構成できる。With this configuration, the rotating mechanism does not require an electromagnetic clutch as in the prior art, and the clutch mechanism 19 (mechanical clutch) has a simple structure, so that it can be inexpensively configured and can be compactly configured. .
なお、上述の実施例において、カム面34a,34b、およ
び係合面35a,35bの形状は、同等の作用を行なうなら
ば、他の形状で構成するもよく、実施例の構造に限定さ
れるものではない。In the above-described embodiment, the cam surfaces 34a, 34b and the engagement surfaces 35a, 35b may be configured in other shapes as long as they have the same effect, and are not limited to the structure of the embodiment. Not a thing.
また、遊星歯車機構17,18も複数段接続することが可
能であって、実施例の２段に限定されるものではない。Further, the planetary gear mechanisms 17 and 18 can also be connected in a plurality of stages, and are not limited to the two stages of the embodiment.
さらに、実施例ではカーテンを開閉操作する駆動機構
として例示したが、その他負荷のある駆動機構として広
く利用することができる。Further, in the embodiment, the driving mechanism for opening and closing the curtain is exemplified, but it can be widely used as a driving mechanism having other loads.
図面はこの発明の一実施例を示し、 第１図はカーテンの駆動機構の系統図、 第２図はクラッチ機構部分の縦断面図、 第３図イ、ロはカム面の形状とその移動量を示す部分展
開図、 第４図イ、ロは係合面の形状とその係合量を示す部分展
開図である。 18……遊星歯車機構、19……クラッチ機構 20b……サンギャ、21b……プラネタリギャ 22b……インターナルギャ、23b……キャリア 25……軸部、26……可動体 27……スプライン筒軸部、33……スプリング 34a,34b……カム面 35a,35b……係合面 36,39……スプライン、37……出力軸The drawings show one embodiment of the present invention, FIG. 1 is a system diagram of a curtain drive mechanism, FIG. 2 is a longitudinal sectional view of a clutch mechanism portion, and FIGS. 3A and 3B are cam surface shapes and movement amounts thereof. FIG. 4B is a partially developed view showing the shape of the engagement surface and the amount of engagement thereof. 18 …… Planetary gear mechanism, 19 …… Clutch mechanism 20b …… Sangier, 21b …… Planetary gear 22b …… Internal gear, 23b …… Carrier 25 …… Shaft part, 26 …… Movable body 27 …… Spline cylinder 33, springs 34a, 34b, cam surfaces 35a, 35b, engagement surfaces 36, 39, splines, 37, output shaft
Claims (1)
ャリアに出力部とする軸部を連設し、 上記遊星歯車機構のインターナルギャの上記軸部側の側
面に付勢状態で対向して、可動体を接離摺動のみ可能に
対設すると共に、相互の対向面に該可動体を接離移動さ
せるカム面を形成し、 上記可動体の中心部には、前記軸部を挿通し、外周面に
スプラインを刻設したスプライン筒軸部を、相対回動の
み自在にして連結し、 上記可動体と前記キャリアとの対向面の相互には、前記
カム面による移動量より係合量が少ない係合面を形成
し、 前記スプライン筒軸部の移動側には、出力軸を対設し、 この出力軸の対向軸端には前記カム面の移動量で前記ス
プライン筒軸部のスプラインと嵌合・非嵌合されるスプ
ラインを形成した 駆動機構。1. A planetary gear mechanism carrier having a sun gear as an input portion is connected to a shaft portion serving as an output portion, and is opposed to a side surface of the internal gear of the planetary gear mechanism on the shaft portion side in a biased state. The movable body is provided to face the movable body only so that the movable body can move toward and away from the movable body, and a cam surface for moving the movable body toward and away from the movable body is formed. The shaft portion is inserted through the central portion of the movable body. Then, the spline cylinder shaft portion having the spline engraved on the outer peripheral surface is connected so that only relative rotation is possible, and the opposing surfaces of the movable body and the carrier are engaged with each other by the movement amount by the cam surface. An engaging surface having a small amount is formed, and an output shaft is provided on the moving side of the spline cylinder shaft portion, and the opposite shaft end of the output shaft has a movement amount of the cam surface that corresponds to the movement amount of the spline cylinder shaft portion. A drive mechanism that forms a spline that is mated or non-mated with the spline.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22002387A JPH0817734B2 (en) | 1987-09-02 | 1987-09-02 | Drive mechanism |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP22002387A JPH0817734B2 (en) | 1987-09-02 | 1987-09-02 | Drive mechanism |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS6462110A JPS6462110A (en) | 1989-03-08 |
| JPH0817734B2 true JPH0817734B2 (en) | 1996-02-28 |
Family
ID=16744723
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP22002387A Expired - Fee Related JPH0817734B2 (en) | 1987-09-02 | 1987-09-02 | Drive mechanism |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPH0817734B2 (en) |
Families Citing this family (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH03280907A (en) * | 1990-03-29 | 1991-12-11 | Oi Seisakusho Co Ltd | Opening/closing device for curtain |
| US5129671A (en) * | 1991-01-25 | 1992-07-14 | Eaton Corporation | Vehicle suspension with auxiliary leaf spring with load control system |
| US5137300A (en) * | 1991-01-25 | 1992-08-11 | Eaton Corporation | Vehicle suspension with auxiliary leaf spring and squat control system |
| CN100374058C (en) * | 2004-12-03 | 2008-03-12 | 揭雪强 | Driving mechanism of common curtain machine |
| CN109681550A (en) * | 2019-02-01 | 2019-04-26 | 上海普英特高层设备股份有限公司 | Brake lock mechanism |
-
1987
- 1987-09-02 JP JP22002387A patent/JPH0817734B2/en not_active Expired - Fee Related
Also Published As
| Publication number | Publication date |
|---|---|
| JPS6462110A (en) | 1989-03-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP2971071B2 (en) | Actuator for friction engagement device | |
| US8037984B2 (en) | Four-wheel-drive-vehicle driving force distribution apparatus | |
| JP4260278B2 (en) | V pulley control mechanism for belt type continuously variable transmission | |
| US7753184B2 (en) | Bidirectional clutch mechanism | |
| JPH02154848A (en) | Belt type continuously variable transmission | |
| US2349410A (en) | Variable speed epicyclic gearing | |
| JPH0817734B2 (en) | Drive mechanism | |
| JP2023041927A (en) | Power transmission path switching device | |
| JP2769607B2 (en) | Driving force transmission mechanism | |
| CA2317335A1 (en) | Differential mechanism | |
| JP2558534B2 (en) | Continuously variable transmission | |
| KR0182816B1 (en) | Clutch device | |
| JPS62502906A (en) | Transmission device for automobiles | |
| JP3694945B2 (en) | Transmission | |
| JP4413310B2 (en) | V pulley control mechanism for belt type continuously variable transmission | |
| JPH0546804B2 (en) | ||
| JP3168906B2 (en) | Clutch device | |
| JPH059887Y2 (en) | ||
| GB2384834A (en) | Gear shifting mechanism having a shift drum positioned by compression springs | |
| JPS62242163A (en) | Planetary change gear | |
| JP2021196042A (en) | Dog clutch | |
| JP2744038B2 (en) | Belt-type continuously variable transmission | |
| JPH11166361A (en) | Clutch device | |
| JP2001124191A (en) | Planetary shift mechanism | |
| JPH06280957A (en) | Continuously variable transmission with friction wheel |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| LAPS | Cancellation because of no payment of annual fees |