JPH0548371B2 - - Google Patents

Info

Publication number
JPH0548371B2
JPH0548371B2 JP59162218A JP16221884A JPH0548371B2 JP H0548371 B2 JPH0548371 B2 JP H0548371B2 JP 59162218 A JP59162218 A JP 59162218A JP 16221884 A JP16221884 A JP 16221884A JP H0548371 B2 JPH0548371 B2 JP H0548371B2
Authority
JP
Japan
Prior art keywords
gear
shaft
shaft portion
cam
input shaft
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 - Lifetime
Application number
JP59162218A
Other languages
Japanese (ja)
Other versions
JPS6141041A (en
Inventor
Shigeru Koizumi
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Mitsui Kinzoku ACT Corp
Original Assignee
Ohi Seisakusho Co Ltd
Priority date (The priority date 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 date listed.)
Filing date
Publication date
Application filed by Ohi Seisakusho Co Ltd filed Critical Ohi Seisakusho Co Ltd
Priority to JP16221884A priority Critical patent/JPS6141041A/en
Publication of JPS6141041A publication Critical patent/JPS6141041A/en
Publication of JPH0548371B2 publication Critical patent/JPH0548371B2/ja
Granted legal-status Critical Current

Links

Classifications

    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H3/00—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion
    • F16H3/02—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion
    • F16H3/20—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear
    • F16H3/22—Toothed gearings for conveying rotary motion with variable gear ratio or for reversing rotary motion without gears having orbital motion exclusively or essentially using gears that can be moved out of gear with gears shiftable only axially
    • E—FIXED CONSTRUCTIONS
    • E05—LOCKS; KEYS; WINDOW OR DOOR FITTINGS; SAFES
    • E05F—DEVICES FOR MOVING WINGS INTO OPEN OR CLOSED POSITION; CHECKS FOR WINGS; WING FITTINGS NOT OTHERWISE PROVIDED FOR, CONCERNED WITH THE FUNCTIONING OF THE WING
    • E05F15/00—Power-operated mechanisms for wings
    • E05F15/60—Power-operated mechanisms for wings using electrical actuators
    • E05F15/603—Power-operated mechanisms for wings using electrical actuators using rotary electromotors

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Structure Of Transmissions (AREA)
  • Power-Operated Mechanisms For Wings (AREA)

Description

【発明の詳細な説明】 （産業上の利用分野） 本発明は、モータ側に連結された入力軸の回転
を、出力軸に伝達して自動車の窓ガラス、スライ
ドドア等に開閉体を開閉する駆動伝達装置に関す
る。[Detailed Description of the Invention] (Industrial Application Field) The present invention transmits the rotation of an input shaft connected to a motor side to an output shaft to open and close an opening/closing body on a car window glass, sliding door, etc. This invention relates to a drive transmission device.

（従来の技術） 従来の駆動伝達装置、例えばパワー式ウインド
レギユレータに使用される駆動伝達装置は、実公
昭58−17113号に示すように窓ガラスの開閉動作
の全区間において、モータ側に連結された入力軸
の回転を常に一定の減速比で出力軸に伝達するよ
うに構成されているのが一般的である。(Prior Art) A conventional drive transmission device, for example, a drive transmission device used in a power type window regulator, has a motor side that is connected to the motor side during the entire window glass opening/closing operation, as shown in Utility Model Publication No. 58-17113. Generally, the configuration is such that the rotation of the connected input shaft is always transmitted to the output shaft at a constant reduction ratio.

（発明が解決しようとする問題点） 一般に、自動車の窓ガラスを開閉する際に、全
閉位置近傍から全閉位置までの閉動作最終段階お
よび全閉位置から全閉位置近傍までの開動作初期
段階においては、窓ガラスと枠との摩擦、窓ガラ
スとシールドラバーとの密着等があるため、窓ガ
ラスを開閉するためには大きな駆動力が必要であ
る。また、寒冷地等において窓ガラスが連結した
際には、さらに大きな駆動力が必要になる。(Problems to be Solved by the Invention) Generally, when opening and closing the window glass of a car, the final stage of the closing operation from near the fully closed position to the fully closed position, and the initial stage of the opening operation from the fully closed position to the vicinity of the fully closed position. At this stage, there is friction between the window glass and the frame, and close contact between the window glass and the shield rubber, so a large driving force is required to open and close the window glass. Further, when window glasses are connected in a cold region, an even greater driving force is required.

しかしながら、パワー式ウインドレギユレータ
に使用される上記従来の駆動伝達装置において
は、常に減速比が一定であるため、全閉位置近傍
から全閉位置の範囲内で駆動力不足により窓ガラ
スを動かすことができないことが起つたり、窓ガ
ラスが凍結した場合には、モータに大きな負荷が
かかつてモータが故障してしまうことがあるとい
う問題点があつた。 However, in the above-mentioned conventional drive transmission device used in power-type window regulators, the reduction ratio is always constant, so the window glass is moved due to insufficient driving force within the range from near the fully closed position to the fully closed position. If something happens that cannot be done or the window glass freezes, there is a problem in that a large load is placed on the motor and the motor may break down.

本発明は、このような問題点に着目して成され
たもので、大きな駆動力を必要とする範囲、すな
わち開閉体の全閉位置から全閉位置近傍までの範
囲においては、該範囲外の場合より減速すること
により、開閉体の開閉動作を確実に行なえる駆動
伝達装置を提供することを目的としている。 The present invention has been made by focusing on such a problem, and in a range that requires a large driving force, that is, from the fully closed position of the opening/closing body to the vicinity of the fully closed position, It is an object of the present invention to provide a drive transmission device that can reliably perform the opening/closing operation of an opening/closing body by decelerating the speed more than necessary.

（発明の構成） かかる目的を達成するための本発明の要旨とす
るところは、モータ側に連結された入力軸の回転
を、出力軸に伝達して開閉体を開閉する駆動伝達
装置において、 前記入力軸に回転力は伝達しつつ軸方向で第１
位置と第２位置とに移動可能な第２軸部を設け、
該第２軸部に小歯車と大歯車とを固設する一方、
前記出力軸に前記第２軸部が第１位置にあるとき
に前記大歯車に噛合する小歯車と、前記第２軸部
が第２位置にあるときに前記小歯車と噛合する大
歯車とを固設し、 前記入力軸の回転とは異なつた速度でしかも該
入力軸に連動するカムギヤを軸方向には移動不能
に保持して前記第２軸部に遊嵌させ、該第２軸部
とカムギヤとの一方にカム溝を設けるとともに他
方に該カム溝に嵌合するカムフオロワとなる突起
を突設し、前記２軸部とカムギヤとの回転数の差
により該第２軸部を前記第１位置または第２位置
に切換保持する変速機構としたことを特徴とする
駆動伝達装置に存する。(Structure of the Invention) The gist of the present invention to achieve the above object is to provide a drive transmission device that opens and closes an opening/closing body by transmitting the rotation of an input shaft connected to a motor side to an output shaft. While transmitting the rotational force to the input shaft,
a second shaft portion movable between the position and the second position;
While fixing a small gear and a large gear to the second shaft portion,
The output shaft includes a small gear that meshes with the large gear when the second shaft portion is in the first position, and a large gear that meshes with the small gear when the second shaft portion is in the second position. A cam gear that is fixedly installed and interlocks with the input shaft at a speed different from the rotation of the input shaft is held immovably in the axial direction and loosely fitted to the second shaft portion, and the cam gear is loosely fitted to the second shaft portion. A cam groove is provided on one side of the cam gear, and a protrusion that becomes a cam follower that fits into the cam groove is provided protrudingly on the other side, and the difference in rotational speed between the two shaft parts and the cam gear causes the second shaft part to The present invention relates to a drive transmission device characterized by having a transmission mechanism that switches and maintains a position or a second position.

（発明の作用） 第２軸部が第１位置にあるとき入力軸を回転駆
動すると、回転力は第２軸部に固設した大歯車か
ら出力軸の小歯車に伝達されて出力軸が回転駆動
される。出力軸は駆動力は小さいが比較的に早く
回転する。(Operation of the invention) When the input shaft is rotationally driven when the second shaft portion is in the first position, the rotational force is transmitted from the large gear fixed to the second shaft portion to the small gear of the output shaft, causing the output shaft to rotate. Driven. The output shaft has a small driving force, but rotates relatively quickly.

入力軸の回転に連動してカムギヤが回転し、カ
ムギヤと入力軸の第２軸部とが相対的に回転変位
し、第２軸部とカムギヤとは、一方のカム溝と他
方のカムフオロワとなる突起との関係で軸方向に
相対的に変位し、カムギヤは軸方向には変位しな
いので、第２軸部が第２位置へ変位して切り換わ
る。 The cam gear rotates in conjunction with the rotation of the input shaft, and the cam gear and the second shaft portion of the input shaft undergo relative rotational displacement, and the second shaft portion and the cam gear form a cam groove on one side and a cam follower on the other side. Since the cam gear is relatively displaced in the axial direction due to the relationship with the protrusion, and the cam gear is not displaced in the axial direction, the second shaft portion is displaced to the second position and switched.

第２軸部の切換により、入力軸の大歯車と出力
軸の小歯車との噛合が外れ、入力軸の小歯車と出
力軸の大歯車とが噛合する。出力軸は駆動力は大
きいが回転速度は遅く回転する。 By switching the second shaft portion, the large gear on the input shaft and the small gear on the output shaft are disengaged, and the small gear on the input shaft and the large gear on the output shaft are brought into mesh. The output shaft has a large driving force but rotates at a slow rotation speed.

入力軸の第２軸部が第２位置にあるとき、入力
軸の前記とは逆方向に回転駆動すれば、前記とは
逆の動きで出力軸が駆動される。 When the second shaft portion of the input shaft is in the second position, if the input shaft is rotated in the opposite direction, the output shaft is driven in the opposite direction.

（実施例） 以下、図面に基づいて本発明の一実施例を説明
する。(Example) Hereinafter, an example of the present invention will be described based on the drawings.

第１図〜第５図は本発明の一実施例を示してい
る。 1 to 5 show an embodiment of the present invention.

第１図および第２図に示すように、駆動伝達装
置１のケース１０には、入力軸２および出力軸３
が回転可能に支持されている。入力軸２は、軸方
向に移動不能な第１軸部２１と、該第１軸部２１
と一体的に回転するとともに、該第１軸部２１に
対して第１図に示す第１位置と第３図に示す第２
位置との間で軸方向に移動可能な第２軸部２２と
から成つている。 As shown in FIGS. 1 and 2, the case 10 of the drive transmission device 1 includes an input shaft 2 and an output shaft 3.
is rotatably supported. The input shaft 2 includes a first shaft portion 21 that is immovable in the axial direction, and a first shaft portion 21 that is immovable in the axial direction.
and the first position shown in FIG. 1 and the second position shown in FIG. 3 with respect to the first shaft part 21.
and a second shaft portion 22 that is movable in the axial direction between positions.

第１軸部２１には、モータＭのウオームギアＧ
１に噛合した入力側ギア２３が固設されており、
第２軸部２２には小歯車２４と大歯車２５とが固
設されている。 The first shaft portion 21 includes a worm gear G of the motor M.
An input side gear 23 meshed with 1 is fixedly installed,
A small gear 24 and a large gear 25 are fixed to the second shaft portion 22 .

前記出力軸３には、入力軸２の第２軸部２２が
第１位置にある時に大歯車２５と噛合する小歯車
３１と、第２軸部２２が第２位置にある時に小歯
車２４と噛合する大歯車３２と、開閉体の駆動機
構側に連結される駆動ピニオン３３とが固設され
ている。 The output shaft 3 has a small gear 31 that meshes with the large gear 25 when the second shaft portion 22 of the input shaft 2 is in the first position, and a small gear 31 that meshes with the large gear 25 when the second shaft portion 22 of the input shaft 2 is in the second position. A large gear 32 that meshes with the large gear 32 and a drive pinion 33 that is connected to the drive mechanism side of the opening/closing body are fixedly provided.

さらに、前記ケース１０内には、入力軸２の回
転に連動し、開閉体が全閉位置から全閉位置近傍
までの範囲内に位置している時に、入力軸２の第
２軸部２２を前記第２位置に切換保持する変速機
構４が設けられている。 Furthermore, in the case 10, the second shaft portion 22 of the input shaft 2 is connected to the rotation of the input shaft 2, and when the opening/closing body is located within the range from the fully closed position to the vicinity of the fully closed position. A transmission mechanism 4 is provided which switches and maintains the transmission at the second position.

該変速機構４は、ケース１０に回転可能に支持
された軸４１と、軸４１に固設され、前記小歯車
２４と常に噛合するような厚さに形成された第１
変速ギア４２と、軸４１に固設され、第１変速ギ
ア４２とモジユールが同一で、該第１変速ギア４
２より歯数の少ない第２変速ギア４３と、入力軸
２の第２軸部２２に外嵌し、ケース１０に回転可
能に支持され、かつ第２変速ギア４３に噛合した
カムギア４４とから構成されている。 The transmission mechanism 4 includes a shaft 41 rotatably supported by the case 10, and a first shaft fixed to the shaft 41 and formed with a thickness such that it always meshes with the small gear 24.
A speed change gear 42 is fixed to the shaft 41, has the same module as the first speed change gear 42, and has the same module as the first speed change gear 42.
2, and a cam gear 44 that is fitted onto the second shaft portion 22 of the input shaft 2, rotatably supported by the case 10, and meshed with the second transmission gear 43. has been done.

前記第２軸部２２は、カムギア４４に対して回
転可能であるとともに、軸方向に移動可能となつ
ている。 The second shaft portion 22 is rotatable relative to the cam gear 44 and movable in the axial direction.

第４図に示すように、カムギア４４には内側に
カム溝４５が凹設されており、このカム溝４５に
は、第２軸部２２の外周に突設されたカムフオロ
ワとなる突起２２ａが係合している。 As shown in FIG. 4, the cam gear 44 has a cam groove 45 recessed inwardly, and a protrusion 22a, which is a cam follower, is engaged with the cam groove 45. It matches.

該カム溝４５は、入力軸２の第２軸部２２を前
記第１位置に保持する第１水平溝４５ａと、第２
軸部２２を前記第２位置に保持する第２水平溝４
５ｂと、該両水平溝４５ａ，４５ｂを結ぶ傾斜溝
４５ｃとから成つている。 The cam groove 45 includes a first horizontal groove 45a that holds the second shaft portion 22 of the input shaft 2 at the first position, and a second horizontal groove 45a that holds the second shaft portion 22 of the input shaft 2 at the first position.
a second horizontal groove 4 that holds the shaft portion 22 in the second position;
5b, and an inclined groove 45c connecting both horizontal grooves 45a and 45b.

また、入力軸２の第２軸部２２が第１位置と第
２位置との間で変位してギアチエンジがスムーズ
に行なわれるように、小歯車２４、大歯車２５、
第１変速ギア４２、大歯車３２および小歯車３１
は、すべてはすば歯車となつている。小歯車２
４、大歯車３２および第１変速ギア４２のねじれ
角は同じであり、かつ大歯車２５および小歯車３
１のねじれ角も同じである。 In addition, a small gear 24, a large gear 25,
First transmission gear 42, large gear 32 and small gear 31
are all helical gears. Small gear 2
4. The helix angles of the large gear 32 and the first transmission gear 42 are the same, and the large gear 25 and the small gear 3
The torsion angle of 1 is also the same.

このねじれ角は以下のようにして求められる。 This twist angle is determined as follows.

第５図に示すように、入力軸２が回転し、大歯
車２５がx°回転すると、その円周はｘ／（360）×
πd25だけ進む。各歯車の厚みはＴ＝const.である
ので、大歯車２５のねじれ角をβ25とすると、 Ｔ／ｘ／360×πd25＝tanβ25 ……(1) となる。 As shown in Fig. 5, when the input shaft 2 rotates and the large gear 25 rotates x degrees, its circumference becomes x/(360) x
Advance by πd 25 . Since the thickness of each gear is T=const., if the helix angle of the large gear 25 is β25 , then T/x/360× πd25 = tanβ25 (1).

これに対して、小歯車２４もx°回転するので、
小歯車２４のねじれ角をβ24とすると、 Ｔ／ｘ／360×πd24＝tanβ24 ……(2) となる。 On the other hand, since the pinion 24 also rotates x°,
If the helix angle of the pinion 24 is β 24 , then T/x/360×πd 24 =tanβ 24 (2).

(1)、(2)式より、 d25／d24＝tanβ24／tanβ25 ……(3) となる。 From equations (1) and (2), d 25 /d 24 =tanβ 24 /tanβ 25 ...(3).

(3)式が成り立つように小歯車２４のねじれ角
β24および大歯車２５のねじれ角β25を定めれば、
ギアチエンジがスムーズに行なわれる。 If the helix angle β 24 of the small gear 24 and the helix angle β 25 of the large gear 25 are determined so that equation (3) holds, then
Gear changes are performed smoothly.

なお、前記ねじれ角β24、β25に合わせてカムギ
ア４４のカム溝４５の傾斜溝４５ｃの傾斜角度を
決めればよい。 Note that the inclination angle of the inclined groove 45c of the cam groove 45 of the cam gear 44 may be determined in accordance with the torsion angles β 24 and β 25 .

以下、作用を説明する。 The action will be explained below.

第１図に示すように、入力軸２の第２軸部２２
が第１位置にある状態において、不図示のスイツ
チをオンにすると、モータＭが回転しウオームギ
アＧ１が回転する。ウオームギアＧ１の回転によ
つて、入力側ギア２３、入力軸２の第１軸部２１
および第２軸部２２が回転し、小歯車２４および
大歯車２５が回転する。 As shown in FIG. 1, the second shaft portion 22 of the input shaft 2
When a switch (not shown) is turned on while the motor is in the first position, the motor M rotates and the worm gear G1 rotates. Due to the rotation of the worm gear G1, the input side gear 23 and the first shaft portion 21 of the input shaft 2
Then, the second shaft portion 22 rotates, and the small gear 24 and the large gear 25 rotate.

大歯車２５の回転によつて、小歯車３１、出力
軸３および駆動ピニオン３３が回転する。該駆動
ピニオン３３の回転が開閉体の駆動機構に伝達さ
れ、開閉体が駆動される。 The rotation of the large gear 25 causes the small gear 31, output shaft 3, and drive pinion 33 to rotate. The rotation of the drive pinion 33 is transmitted to the drive mechanism of the opening/closing body, thereby driving the opening/closing body.

一方、小歯車２４の回転によつて、第１変速ギ
ア４２、軸４１、第２変速ギア４３およびカムギ
ア４４が回転する。ここで、第２変速ギア４３の
歯数が第１変速ギア４２の歯数より少なくなつて
いるので、カムギア４４の回転速度は、入力軸２
の第２軸部２２の回転速度とは異なつている。 On the other hand, the rotation of the small gear 24 causes the first transmission gear 42, shaft 41, second transmission gear 43, and cam gear 44 to rotate. Here, since the number of teeth of the second transmission gear 43 is smaller than the number of teeth of the first transmission gear 42, the rotation speed of the cam gear 44 is lower than that of the input shaft 2.
The rotational speed of the second shaft portion 22 is different from that of the second shaft portion 22 .

したがつて、第２軸部２２とカムギア４４との
間に相対的な回転変位が生じ、第２軸部２２の突
起２２ａがカムギア４４のカム溝４５内を移動す
る。 Therefore, a relative rotational displacement occurs between the second shaft portion 22 and the cam gear 44, and the protrusion 22a of the second shaft portion 22 moves within the cam groove 45 of the cam gear 44.

すなわち、開閉体が全閉位置から全閉位置近傍
までの範囲外に位置している時には、突起２２ａ
がカム溝４５の第１水平溝４５ａ内で移動してお
り、入力軸２の第２軸部２２が第１位置に保持さ
れている。 That is, when the opening/closing body is located outside the range from the fully closed position to the vicinity of the fully closed position, the protrusion 22a
is moving within the first horizontal groove 45a of the cam groove 45, and the second shaft portion 22 of the input shaft 2 is held at the first position.

したがつて、第２軸部２２の大歯車２５が出力
軸３の小歯車３１に噛合し、入力軸２の回転が増
速されて出力軸３に伝達される。 Therefore, the large gear 25 of the second shaft portion 22 meshes with the small gear 31 of the output shaft 3, and the rotation of the input shaft 2 is accelerated and transmitted to the output shaft 3.

そして、開閉体が前記範囲に近づくと、突起２
２ａがカム溝４５の傾斜溝４５ｃ内に入り、該傾
斜溝４５ｃ内を第２水平溝４５ｂに向つて移動す
る。この移動によつて入力軸２の第２軸部２２が
第１位置から第２位置に向つて変位する。 When the opening/closing body approaches the above range, the protrusion 2
2a enters the inclined groove 45c of the cam groove 45 and moves within the inclined groove 45c toward the second horizontal groove 45b. This movement causes the second shaft portion 22 of the input shaft 2 to be displaced from the first position toward the second position.

開閉体が前記範囲内に入つた時点で、突起２２
ａが第２水平溝４５ｂ内に入り、第２軸部２２の
第２位置側への変位が完了する。この変位によつ
て、第２軸部２２の大歯車２５が出力軸３の小歯
車３１から外れ、第２軸部２２の小歯車２４が出
力軸の大歯車３２に噛合する。これによつて、入
力軸２の回転が減速されて出力軸３に伝達される
ので、大きな駆動力が出力軸３に伝達される。 When the opening/closing body enters the range, the protrusion 22
a enters the second horizontal groove 45b, and the displacement of the second shaft portion 22 toward the second position is completed. Due to this displacement, the large gear 25 of the second shaft portion 22 is disengaged from the small gear 31 of the output shaft 3, and the small gear 24 of the second shaft portion 22 meshes with the large gear 32 of the output shaft. As a result, the rotation of the input shaft 2 is decelerated and transmitted to the output shaft 3, so that a large driving force is transmitted to the output shaft 3.

そして、開閉体が前記範囲内に位置している間
は、突起２２ａは第２水平溝４５ｂ内にあり、入
力軸２の第２軸部２２が第２位置に保持される。 While the opening/closing body is located within the range, the protrusion 22a is within the second horizontal groove 45b, and the second shaft portion 22 of the input shaft 2 is held at the second position.

逆に、開閉体が前記範囲外に移動する際には、
突起２２ａが第２水平溝４５ｂから傾斜溝４５ｃ
内に入り、該傾斜溝４５ｃ内を第１水平溝４５ａ
に向つて移動する。 Conversely, when the opening/closing body moves outside the above range,
The protrusion 22a extends from the second horizontal groove 45b to the inclined groove 45c.
the first horizontal groove 45a inside the inclined groove 45c.
move towards.

この移動によつて、第２軸部２２が第２位置か
ら第１位置に向つて変位し、該変位によつて、第
２軸部２２の大歯車２５が出力軸３の小歯車３１
に再び噛合する。なお、第１変速ギア４２は入力
側ギア２３に噛合わせてもよい。この場合、相方
とも平歯車となる。 Due to this movement, the second shaft portion 22 is displaced from the second position toward the first position, and due to this displacement, the large gear 25 of the second shaft portion 22 is moved to the small gear 31 of the output shaft 3.
engage again. Note that the first speed change gear 42 may mesh with the input side gear 23. In this case, both partners are spur gears.

次に本発明に係る駆動伝達装置１をパワー式ウ
インドレギユレータの駆動部として使用した応用
例を第６図および第７図に基づいて説明する。 Next, an application example in which the drive transmission device 1 according to the present invention is used as a drive section of a power type window regulator will be explained based on FIGS. 6 and 7.

駆動伝達装置１の駆動ピニオン３３は、パワー
式ウインドレギユレータ５のセクタギア５１に噛
合しており、該セクタギア５１にはメインアーム
５２が固着されている。駆動ピニオン３３が回転
すると、セクタギア５１を介してメインアーム５
２が軸５３を中心に回動し、該回動によつて窓ガ
ラス５４が昇降する。 The drive pinion 33 of the drive transmission device 1 meshes with a sector gear 51 of the power type wind regulator 5, and a main arm 52 is fixed to the sector gear 51. When the drive pinion 33 rotates, the main arm 5
2 rotates around a shaft 53, and the window glass 54 moves up and down as a result of this rotation.

窓ガラス５４が昇降する際に、窓ガラス５４が
第７図に示すような全閉位置近傍から全閉位置ま
での範囲内に位置している時には、窓ガラス５４
が該範囲外にある場合に比べて大きな駆動力が駆
動ピニオン３３からセクタギア５１に伝達され
る。 When the window glass 54 moves up and down, if the window glass 54 is located within the range from near the fully closed position to the fully closed position as shown in FIG.
A larger driving force is transmitted from the drive pinion 33 to the sector gear 51 than when the is outside the range.

なお、本発明に係る駆動伝達装置１は第８図に
示すようなスライドドア６などの開閉体のオート
システムの駆動部として使用することもできる。 The drive transmission device 1 according to the present invention can also be used as a drive unit of an automatic system for opening and closing objects such as a sliding door 6 as shown in FIG.

（発明の効果） 本発明に係る駆動伝達装置によれば、開閉体が
全閉位置から全閉位置近傍までの範囲内に位置し
ている時には、変速機構が入力軸を第２位置に切
換保持し、これによつて開閉体が前記範囲外にあ
る場合に比べて大きな駆動力が入力軸から出力軸
に伝達されるので、開閉体の開閉動作を確実に行
なえる。(Effects of the Invention) According to the drive transmission device according to the present invention, when the opening/closing body is located within the range from the fully closed position to the vicinity of the fully closed position, the transmission mechanism switches and holds the input shaft in the second position. However, as a result, a larger driving force is transmitted from the input shaft to the output shaft than when the opening/closing body is outside the above range, so that the opening/closing operation of the opening/closing body can be performed reliably.

【図面の簡単な説明】[Brief explanation of drawings]

第１図〜第５図は本発明の一実施例を示してお
り、第１図は縦断面図、第２図は歯車列の平面
図、第３図は、第１図と同様の縦断面図、第４図
は変速機構の説明図、第５図はギアチエンジの説
明図、第６図および第７図は本発明に係る駆動伝
達装置をパワー式ウインドレギユレータの駆動部
として使用した応用例を示しており、第６図は要
部の拡大平面図、第７図は取付状態を示す正面
図、第８図は本発明に係る駆動伝達装置を使用可
能なスライドドア式の自動車の側面図である。 １……駆動伝達装置、２……入力軸、３……出
力軸、４……変速機構、Ｍ……モータ、２４……
小歯車、２５……大歯車、３１……小歯車、３２
……大歯車。 1 to 5 show an embodiment of the present invention, FIG. 1 is a longitudinal cross-sectional view, FIG. 2 is a plan view of a gear train, and FIG. 3 is a longitudinal cross-section similar to that in FIG. 1. Fig. 4 is an explanatory diagram of the transmission mechanism, Fig. 5 is an explanatory diagram of the gear change, and Figs. 6 and 7 are applications in which the drive transmission device according to the present invention is used as a drive part of a power type wind regulator. An example is shown in which Fig. 6 is an enlarged plan view of the main parts, Fig. 7 is a front view showing the installed state, and Fig. 8 is a side view of a sliding door type automobile in which the drive transmission device according to the present invention can be used. It is a diagram. 1... Drive transmission device, 2... Input shaft, 3... Output shaft, 4... Speed change mechanism, M... Motor, 24...
Small gear, 25... Large gear, 31... Small gear, 32
...Big gear.

Claims (1)

【特許請求の範囲】 １ モータ側に連結された入力軸の回転を、出力
軸に伝達して開閉体を開閉する駆動伝達装置にお
いて、 前記入力軸に回転力は伝達しつつ軸方向で第１
位置と第２位置とに移動可能な第２軸部を設け、
該第２軸部に小歯車と大歯車とを固設する一方、
前記出力軸に前記第２軸部が第１位置にあるとき
に前記大歯車に噛合する小歯車と、前記第２軸部
が第２位置にあるときに前記小歯車と噛合する大
歯車とを固設し、 前記入力軸の回転とは異なつた速度でしかも該
入力軸に連動するカムギヤを軸方向には移動不能
に保持して前記第２軸部に遊嵌させ、該第２軸部
とカムギヤとの一方にカム溝を設けるとともに他
方に該カム溝に嵌合するカムフオロワとなる突起
を突設し、前記２軸部とカムギヤとの回転数の差
により該第２軸部を前記第１位置または第２位置
に切換保持する変速機構としたことを特徴とする
駆動伝達装置。[Scope of Claims] 1. A drive transmission device that opens and closes an opening/closing body by transmitting the rotation of an input shaft connected to a motor side to an output shaft, comprising
a second shaft portion movable between the position and the second position;
While fixing a small gear and a large gear to the second shaft portion,
The output shaft includes a small gear that meshes with the large gear when the second shaft portion is in the first position, and a large gear that meshes with the small gear when the second shaft portion is in the second position. A cam gear that is fixedly installed and interlocks with the input shaft at a speed different from the rotation of the input shaft is held immovably in the axial direction and loosely fitted to the second shaft portion, and the cam gear is loosely fitted to the second shaft portion. A cam groove is provided on one side of the cam gear, and a protrusion that becomes a cam follower that fits into the cam groove is provided protrudingly on the other side, and the difference in rotational speed between the two shaft parts and the cam gear causes the second shaft part to A drive transmission device characterized by having a transmission mechanism that switches and holds the position or the second position.
JP16221884A 1984-07-31 1984-07-31 Driving transmission apparatus Granted JPS6141041A (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP16221884A JPS6141041A (en) 1984-07-31 1984-07-31 Driving transmission apparatus

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP16221884A JPS6141041A (en) 1984-07-31 1984-07-31 Driving transmission apparatus

Publications (2)

Publication Number Publication Date
JPS6141041A JPS6141041A (en) 1986-02-27
JPH0548371B2 true JPH0548371B2 (en) 1993-07-21

Family

ID=15750205

Family Applications (1)

Application Number Title Priority Date Filing Date
JP16221884A Granted JPS6141041A (en) 1984-07-31 1984-07-31 Driving transmission apparatus

Country Status (1)

Country Link
JP (1) JPS6141041A (en)

Families Citing this family (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH0792888B2 (en) * 1989-12-06 1995-10-09 シャープ株式会社 Rotating drum device
JP6548614B2 (en) * 2016-08-08 2019-07-24 オムロンオートモーティブエレクトロニクス株式会社 Opening and closing body control device and opening and closing body control method

Family Cites Families (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS536647U (en) * 1976-07-02 1978-01-20

Also Published As

Publication number Publication date
JPS6141041A (en) 1986-02-27

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