JP4619680B2

JP4619680B2 - Drive device

Info

Publication number: JP4619680B2
Application number: JP2004116859A
Authority: JP
Inventors: 裕日野
Original assignee: Sharp Corp
Current assignee: Sharp Corp
Priority date: 2004-04-12
Filing date: 2004-04-12
Publication date: 2011-01-26
Anticipated expiration: 2024-04-12
Also published as: JP2005299795A

Description

本発明は、画像印字装置や画像読取装置などで、移動する部分を駆動する駆動装置、特に一つのモータで複数の部分を個別に駆動する切替機構を有する駆動装置に関する。 The present invention relates to a driving device that drives a moving part in an image printing apparatus, an image reading apparatus, and the like, and more particularly, to a driving device that has a switching mechanism that individually drives a plurality of parts with one motor.

従来から、ファクシミリや複写機などのような画像印字装置や画像読取装置では、印字機構や読取りセンサ、原稿や出力用紙など、各部分を動作のモードに応じて移動させている。小型化やコスト低減の要求を満たすため、複数のモードに応じて駆動源からの動力を一方および他方搬送機構のうちのいずれか片方、または両方の搬送機構に伝達して用紙を搬送するための駆動装置において、遊星レバーとカムとを組み合わせて実現している例がある（たとえば、特許文献１参照）。 2. Description of the Related Art Conventionally, in an image printing apparatus or image reading apparatus such as a facsimile or a copying machine, each part such as a printing mechanism, a reading sensor, a document, and output paper is moved in accordance with an operation mode. In order to meet the demands for miniaturization and cost reduction, the power from the drive source is transmitted to one or both of the one or the other transport mechanism according to multiple modes to transport the paper. There is an example in which a driving lever is realized by combining a planetary lever and a cam (see, for example, Patent Document 1).

図１０〜図１４は、特許文献１に開示されている考え方を適用する駆動装置の概略的な構成を示す。この駆動装置は、ファクシミリ装置に用いられ、一つのモータ１で送信側ローラ類、受信側ローラ類、またはその両方を切替えて駆動することを可能とする。なお、実施形態として説明する図１〜図９も含めて、図１〜図１４では、図２および図１１を除き、上下に重なる部分も同様に表示する。 10 to 14 show a schematic configuration of a drive device to which the concept disclosed in Patent Document 1 is applied. This driving device is used in a facsimile machine, and enables one motor 1 to switch and drive the transmission side rollers, the reception side rollers, or both. In addition, in FIGS. 1-14 including FIGS. 1-9 demonstrated as embodiment, the part which overlaps up and down is similarly displayed except FIG. 2 and FIG.

図１０は、モードの切替えの際に移動する部分を、異なる位置の状態を重複させて示す。モータ１の駆動力は、受信側の太陽ギヤ２を介して受信側遊星ギヤ３に伝達される。受信側遊星ギヤ３は、受信側遊星レバー４の一方端部に軸支される。受信側遊星ギヤ３は、受信モードで、駆動力を受信側減速ギヤ５へ伝達する。受信側減速ギヤ５から先は、図示を省略している受信用ローラ類へと駆動力が伝達される。また、モータ１の駆動力は、送信側の太陽ギヤ６を介して、送信側遊星ギヤ７に伝達される。送信側遊星ギヤ７は、送信側遊星レバー８の一方端部に軸支される。送信側遊星ギヤ８は、送信モードで、駆動力を送信側減速ギヤ９へ伝達する。送信側減速ギヤ９から先は、図示を省略している送信用ローラ類へと駆動力が伝達される。 FIG. 10 shows the part that moves when the mode is switched, with the states at different positions overlapped. The driving force of the motor 1 is transmitted to the receiving planetary gear 3 via the receiving sun gear 2. The receiving planetary gear 3 is pivotally supported at one end of the receiving planetary lever 4. The reception-side planetary gear 3 transmits driving force to the reception-side reduction gear 5 in the reception mode. From the receiving side reduction gear 5, the driving force is transmitted to the receiving rollers not shown. The driving force of the motor 1 is transmitted to the transmission-side planetary gear 7 via the transmission-side sun gear 6. The transmission-side planetary gear 7 is pivotally supported at one end of the transmission-side planetary lever 8. The transmission-side planetary gear 8 transmits driving force to the transmission-side reduction gear 9 in the transmission mode. From the transmission side reduction gear 9, the driving force is transmitted to the transmission rollers not shown.

受信側遊星レバー４および送信側遊星レバー８の一方端部と他方端部との中間部分は、太陽ギヤ２，６の回転軸を支点として、それぞれ揺動変位が可能である。受信側遊星レバー４が揺動変位すると、受信側遊星ギヤ３は、太陽ギヤ２と噛合する状態を保ちながら、受信側減速ギヤ５と噛合する位置と、カムギヤ１０と噛合する位置との間を移動する。送信側遊星レバー８が揺動変位すると送信側遊星ギヤ３は、太陽ギヤ６と噛合する状態を保ちながら、送信側減速ギヤ９と噛合する位置と、噛合しない位置との間を移動する。カムギヤ１０に関しては、カムスプリング１１とカムスイッチ１２とが設けられる。駆動力の発生源であるモータ１が図の反時計回り方向に回動すると、受信側遊星レバー４が反時計回り方向に揺動変位し、受信側遊星レバー４の一方端部に軸支されている受信側遊星ギヤ３がカムギヤ１０に噛合し、カムギヤ１０は反時計回り方向に回転する。 The intermediate portion between one end and the other end of the receiving planetary lever 4 and the transmitting planetary lever 8 can be oscillated and displaced with the rotation shafts of the sun gears 2 and 6 as fulcrums. When the receiving planetary lever 4 is oscillated and displaced, the receiving planetary gear 3 is maintained in a state of meshing with the sun gear 2 and between the position of meshing with the receiving reduction gear 5 and the position of meshing with the cam gear 10. Moving. When the transmission-side planetary lever 8 is oscillated and displaced, the transmission-side planetary gear 3 moves between a position where the transmission-side planetary gear 3 meshes with the transmission-side reduction gear 9 and a position where the transmission-side planetary gear 3 does not mesh. For the cam gear 10, a cam spring 11 and a cam switch 12 are provided. When the motor 1 that is the driving force generation source rotates counterclockwise in the figure, the receiving planetary lever 4 swings and displaces counterclockwise and is pivotally supported by one end of the receiving planetary lever 4. The receiving planetary gear 3 is engaged with the cam gear 10, and the cam gear 10 rotates counterclockwise.

図１１は、カムギヤ１０の形状を示す。（ａ）は正面視、（ｂ）は側面視の形状をそれぞれ示す。カムギヤ１０には、遊星レバー規制面１０ａとカムスプリング当接面１０ｂとが形成されている。図１０に示すように、遊星ギヤ３がカムギヤ１０に噛合して、カムギヤ１０が反時計回り方向に回転すると、カムスイッチ１２はカムギヤの遊星レバー規制面１０ａに当接することによって、ＯＦＦからＯＮへ変化する。このカムスイッチ１２からのスイッチ信号のＯＦＦからＯＮへの変化を監視することで、カムギヤ１０の初期位置を知ることができる。初期位置検出後は、一定量モータ１を回動させることによって、カムギヤ１０を受信モード、送信モード、またはコピーモードにそれぞれ対応する状態に角変位させることができる。 FIG. 11 shows the shape of the cam gear 10. (A) shows the shape of the front view, and (b) shows the shape of the side view. The cam gear 10 is formed with a planetary lever restricting surface 10a and a cam spring contact surface 10b. As shown in FIG. 10, when the planetary gear 3 meshes with the cam gear 10 and the cam gear 10 rotates counterclockwise, the cam switch 12 comes into contact with the planetary lever restricting surface 10a of the cam gear, thereby turning from OFF to ON. Change. By monitoring the change of the switch signal from the cam switch 12 from OFF to ON, the initial position of the cam gear 10 can be known. After the initial position is detected, the cam gear 10 can be angularly displaced to a state corresponding to the reception mode, transmission mode, or copy mode by rotating the motor 1 by a certain amount.

各モード位置へカムギヤ１０を角変位させるためのモータ１の回動量は、モータ１からカムギヤ１０までの減速比等によって決定される。たとえば、受信モード、送信モードおよびコピーモードの順に、６４０．３°、２３８２．３°および１８４１．９°回動することで、各モードに対応する角変位をそれぞれ実現している。このとき、カムスプリング１１は、カムギヤ１０のカムスプリング当接面１０ｂを押さえ込んでおり、振動その他外乱等によってカムギヤ１０が目的の角度以外に角変位することを防いでいる。 A rotation amount of the motor 1 for angularly displacing the cam gear 10 to each mode position is determined by a reduction ratio from the motor 1 to the cam gear 10 or the like. For example, the angular displacement corresponding to each mode is realized by rotating 640.3 °, 2382.3 °, and 1841.9 ° in the order of the reception mode, the transmission mode, and the copy mode. At this time, the cam spring 11 presses the cam spring abutting surface 10b of the cam gear 10 to prevent the cam gear 10 from being angularly displaced other than the target angle due to vibration or other disturbances.

図１２は、カムギヤ１０が受信モードに対応する角度となる状態を示す。カムギヤ１０を受信モードの状態にして、モータ１を時計回り方向に回転させると、送信側遊星レバー８が時計回り方向に揺動変位し、送信側遊星ギヤ７が送信側減速ギヤ９へ噛合しようとする。しかし、送信側遊星レバーカム側端８ａがカムギヤ１０の遊星レバー規制面１０ａに当接して送信側遊星レバー８の揺動変位を規制し、送信側減速ギヤ９へは駆動力が伝わらない。一方、受信側遊星レバーカム側端４ａはカムギヤ１０の遊星レバー規制面１０ａには当接しないため、受信側遊星レバー４の角変位は規制されず、受信側遊星ギヤ３が受信側減速ギヤ５に噛合し、受信側減速ギヤ５へ駆動力が伝達される。 FIG. 12 shows a state where the cam gear 10 has an angle corresponding to the reception mode. When the cam gear 10 is set in the reception mode and the motor 1 is rotated in the clockwise direction, the transmission-side planetary lever 8 swings and displaces in the clockwise direction, so that the transmission-side planetary gear 7 engages with the transmission-side reduction gear 9. And However, the transmission-side planetary lever cam side end 8 a abuts on the planetary lever restricting surface 10 a of the cam gear 10 to restrict the swinging displacement of the transmission-side planetary lever 8, and no driving force is transmitted to the transmission-side reduction gear 9. On the other hand, the receiving planetary lever cam side end 4 a does not contact the planetary lever restricting surface 10 a of the cam gear 10, so that the angular displacement of the receiving planetary lever 4 is not restricted, and the receiving planetary gear 3 becomes the receiving reduction gear 5. Engage and the driving force is transmitted to the receiving side reduction gear 5.

図１３は、カムギヤ１０が送信モードに対応する角度となる状態を示す。モータ１を時計回り方向に回転させると、受信側遊星レバー４が時計回り方向に揺動変位し、受信側遊星ギヤ３が受信側減速ギヤ５へ噛合しようとする。しかし、受信側遊星レバーカム側端４ａがカムギヤ１０の遊星レバー規制面１０ａに当接して、受信側遊星レバー４の揺動変位を規制し、受信側減速ギヤ５へは駆動力が伝わらない。一方、送信側遊星レバーカム側端８ａはカムギヤ１０の遊星レバー規制面１０ａには当接しないため、送信側遊星レバー８の揺動変位は規制されず、送信側遊星ギヤ７が送信側減速ギヤ９に噛合し、送信側減速ギヤ９へ駆動力が伝達される。 FIG. 13 shows a state where the cam gear 10 has an angle corresponding to the transmission mode. When the motor 1 is rotated in the clockwise direction, the reception-side planetary lever 4 is oscillated and displaced in the clockwise direction, and the reception-side planetary gear 3 tries to mesh with the reception-side reduction gear 5. However, the receiving planetary lever cam side end 4 a abuts on the planetary lever restricting surface 10 a of the cam gear 10 to restrict the swinging displacement of the receiving planetary lever 4, and no driving force is transmitted to the receiving reduction gear 5. On the other hand, the transmission-side planetary lever cam side end 8a does not contact the planetary lever restricting surface 10a of the cam gear 10, so that the swinging displacement of the transmission-side planetary lever 8 is not restricted, and the transmission-side planetary gear 7 is connected to the transmission-side reduction gear 9. And the driving force is transmitted to the transmission side reduction gear 9.

図１４は、カムギヤ１０がコピーモードに対応する角度となる状態を示す。モータ１を時計回り方向に回転させると、受信側遊星レバー４は時計回り方向に揺動変位する。受信側遊星レバーカム側端４ａは、カムギヤ１０の遊星レバー規制面１０ａには当接しないため、受信側遊星レバー４の揺動変位は規制されず、受信側遊星ギヤ３が受信側減速ギヤ５に噛合し、受信側減速ギヤ５へ駆動力が伝達される。一方、送信側遊星レバー８は時計回り方向に揺動変位する。送信側遊星レバーカム側端８ａは、カムギヤ１０の遊星レバー規制面１０ａには当接しないため、送信側遊星レバー８の揺動変位は規制されず、送信側遊星ギヤ７が送信側減速ギヤ９に噛合し、送信側減速ギヤ９へ駆動力が伝達される。 FIG. 14 shows a state where the cam gear 10 is at an angle corresponding to the copy mode. When the motor 1 is rotated in the clockwise direction, the receiving planetary lever 4 is oscillated and displaced in the clockwise direction. Since the receiving side planetary lever cam side end 4 a does not contact the planetary lever regulating surface 10 a of the cam gear 10, the swinging displacement of the receiving side planetary lever 4 is not regulated, and the receiving side planetary gear 3 becomes the receiving side reduction gear 5. Engage and the driving force is transmitted to the receiving side reduction gear 5. On the other hand, the transmitting planetary lever 8 is oscillated and displaced in the clockwise direction. Since the transmission-side planetary lever cam side end 8 a does not contact the planetary lever restricting surface 10 a of the cam gear 10, the swinging displacement of the transmission-side planetary lever 8 is not restricted, and the transmission-side planetary gear 7 becomes the transmission-side reduction gear 9. Engage and drive force is transmitted to the transmission side reduction gear 9.

すなわち、図１０〜図１４に示す駆動装置は、
駆動源である双方向に回転可能なモータ１の動力が伝達されるモータギヤと、
カムと、カムスイッチ１２と、
各搬送機構用に略Ｖ字状の第一および第二遊星レバーである受信側遊星レバー４および送信側遊星レバー８が揺動変位可能にそれぞれ支持され、前記モータギヤとそれぞれ噛合する第一および第二太陽ギヤである太陽ギヤ２，６と、
第一遊星レバーの一方端部に回転可能に軸支され、前記第一太陽ギヤと噛合する第一遊星ギヤである受信側遊星ギヤ３と、
第二遊星レバーの一方端部に回転可能に軸支され，前記第二太陽ギヤと噛合する第二遊星ギヤである送信側遊星ギヤ７と、
前記第一または第二遊星レバーの他方端部が当接するカムである遊星レバー規制面１０ａが設けられるカムギヤ１０とを含んで構成され、
カムスイッチ１２のＯＮ，ＯＦＦを検出してカムギヤ１０を遊星レバー規制面１０ａが所定の位置となるように角変位させて、
第一モードである受信モードでは第二遊星レバーの他方端部がカムギヤ１０に固定されたカムである遊星レバー規制面１０ａに当接して第二遊星レバーの揺動変位が規制され、第一遊星ギヤと一方搬送機構を構成する受信側減速ギヤ５とが噛合し、
第二モードである送信モードでは、第一遊星レバーの他方端部がカムギヤ１０に固定されたカムであり遊星レバー当接面１０ａに当接して第一遊星レバーの回動が規制され、第二遊星ギヤと他方搬送機構を構成する送信側減速ギヤ９とが噛合し、
第三モードであるコピーモードでは、第一および第二遊星レバーの他方端部はともにカムギヤ１０に固定されたカムである遊星レバー規制面１０ａに当接せず、第一および第二遊星ギヤと一方および他方搬送機構の減速ギヤとがそれぞれ噛合し、
第一、第二、および第三モードでは、それぞれ一方搬送機構のみ、他方搬送機構のみ、および両方搬送機構を駆動することを実現している。 That is, the drive device shown in FIGS.
A motor gear to which the power of the bidirectionally rotatable motor 1 as a drive source is transmitted;
A cam, a cam switch 12,
The first and second planetary levers 4 and 8, which are substantially V-shaped first and second planetary levers for each transport mechanism, are supported so as to be swingable and displaceable, and engage with the motor gears respectively. Two sun gears, sun gears 2 and 6,
A receiving planetary gear 3 that is a first planetary gear that is rotatably supported at one end of the first planetary lever and meshes with the first sun gear;
A transmitting planetary gear 7 that is a second planetary gear that is rotatably supported at one end of the second planetary lever and meshes with the second sun gear;
And a cam gear 10 provided with a planetary lever restricting surface 10a which is a cam with which the other end of the first or second planetary lever abuts.
By detecting ON / OFF of the cam switch 12, the cam gear 10 is angularly displaced so that the planetary lever restricting surface 10a is at a predetermined position,
In the reception mode, which is the first mode, the other end of the second planetary lever comes into contact with the planetary lever restricting surface 10a that is a cam fixed to the cam gear 10, and the swinging displacement of the second planetary lever is restricted. The gear and the receiving-side reduction gear 5 constituting the one-side transport mechanism mesh with each other,
In the transmission mode, which is the second mode, the other end of the first planetary lever is a cam fixed to the cam gear 10 and abuts against the planetary lever abutment surface 10a to restrict the rotation of the first planetary lever. The planetary gear and the transmission-side reduction gear 9 constituting the other transport mechanism mesh with each other,
In the copy mode, which is the third mode, the other ends of the first and second planetary levers do not come into contact with the planetary lever restricting surface 10a, which is a cam fixed to the cam gear 10, and the first and second planetary gears The reduction gears of one and the other transport mechanism mesh with each other,
In the first, second, and third modes, it is realized that only one transport mechanism, only the other transport mechanism, and both transport mechanisms are driven.

特開平９−１５００９８５号公報Japanese Patent Laid-Open No. 9-1500985

特許文献１に開示される駆動装置では、切替えを制御するカムの回転位置を検出するために、カムギヤ１０の凹凸部分である遊星レバー規制面１０ａに当接するようなカムスイッチ１２を有しており、カムスイッチ１２がＯＮからＯＦＦになってから一定量カムギヤ１０を回動させることで所定の位置にカムを制御して、モータ１の駆動力を各モードの搬送機構に伝達している。 The drive device disclosed in Patent Document 1 has a cam switch 12 that abuts on a planetary lever restricting surface 10a that is an uneven portion of the cam gear 10 in order to detect the rotational position of a cam that controls switching. Then, after the cam switch 12 is turned from ON to OFF, the cam is controlled to a predetermined position by rotating the cam gear 10 by a certain amount, and the driving force of the motor 1 is transmitted to the transport mechanism in each mode.

このような駆動装置を含むファクシミリ装置などでは、このカムスイッチ１２に付随してカムスイッチケーブルが必要となり、この２点の部品は当該駆動装置の中で比較的大きなコスト比率を占めている。 In a facsimile machine including such a driving device, a cam switch cable is required in association with the cam switch 12, and these two parts occupy a relatively large cost ratio in the driving device.

したがって、本発明はこれを廃止することを目的とし、コスト的に有利な駆動装置を実現する。 Therefore, the present invention aims to eliminate this, and realizes a cost-effective drive device.

すなわち、本発明の目的は、一つのモータを駆動源として、駆動力の伝達経路を切替え可能にし、しかも機構を簡略化することができる駆動装置を提供することである。 That is, an object of the present invention is to provide a driving device that can switch a transmission path of driving force using a single motor as a driving source and can simplify the mechanism.

本発明は、駆動源からの動力を、第１および第２モードギヤ（２５，２９）のいずれか一方および両者に伝達する駆動装置において、
前記駆動源は、正逆回転可能なモータ（２１）と、そのモータ（２１）の回転軸に設けられたモータギヤと、そのモータギヤによって回転される減速ギヤ（３２）とを有し、
前記減速ギヤ（３２）に噛合する第１太陽ギヤ（２２）と、
前記第１太陽ギヤ（２２）と噛合し、前記第１モードギヤ（２５）と噛合、離脱する第１遊星ギヤ（２３）と、
第１遊星レバー（２４）であって、前記第１太陽ギヤ（２２）の軸上に回転可能に設けられ、一方端部に、前記第１遊星ギヤ（２３）が回転可能に設けられ、他方端部に、第１遊星レバーカム端（２４ａ）を有する第１遊星レバー（２４）と、
前記減速ギヤ（３２）に噛合する第２太陽ギヤ（２６）と、
前記第２太陽ギヤ（２６）と噛合し、前記第２モードギヤ（２９）と噛合、離脱する第２遊星ギヤ（２７）と、
第２遊星レバー（２８）であって、前記第２太陽ギヤ（２２）の軸上に回転可能に設けられ、一方端部に、前記第２遊星ギヤ（２７）が回転可能に設けられ、他方端部に、第２遊星レバーカム端（２８ａ）を有する第２遊星レバー（２８）と、
回転可能なカムギヤ（３０）であって、一方面側に、遊星レバー規制面（３０ａ）を有し、他方面側に、円周方向に欠落部分を有しかつ溝に臨む内壁面となっている当接面（３０ｃ）を有するカムギヤ（３０）と、
前記第１遊星ギヤ（２３）と噛合、離脱可能であり、前記カムギヤ（３０）と噛合、離脱可能であるカム切替ギヤ（３４）と、
カム切替レバー（３３）であって、一方端部に、前記カム切替ギヤ（３４）が回転可能に設けられ、他方端部に、前記欠落部分から前記カムギヤ（３０）の径方向の内方と外方とに変位可能である引掛部（３３ａ）を有する前記カム切替レバー（３３）と、
復帰スプリング（３５）であって、前記カム切替レバー（３３）に、前記引掛部（３３ａ）が前記カムギヤ（３０）の径方向の内方へ向かうばね力を与え、
前記モータ（２１）の一方向（反時計方向）回転によって、前記第１遊星ギヤ（２３）がカム切替ギヤ（３４）に噛合して、前記引掛部（３３ａ）は、前記ばね力に抗して前記当接面（３０ｃ）に当接し、前記カム切替ギヤ（３４）が前記カムギヤ（３０）に噛合し、前記引掛部（３３ａ）が前記欠落部分では、前記ばね力に抗して径方向の外方に変位して前記カム切替ギヤ（３４）が前記カムギヤ（３０）から離脱し（図４、図５）、
前記モータ（２１）の他方向（時計方向）回転によって、前記第１遊星ギヤ（２３）が前記カム切替ギヤ（３４）から離脱し、前記引掛部（３３ａ）を、前記欠落部分から、前記ばね力によって、前記カムギヤ（３０）の径方向の内方に入り込ませる（図６）、復帰スプリング（３５）とを備え、
前記カムギヤ（３０）の前記遊星レバー規制面（３０ａ）は、前記モータ（２１）の前記一方向回転によって回転される前記カムギヤ（３０）の回転方向に順に、前記欠落部分から第１〜第３モード位置を有し、
前記モータ（２１）の前記他方向回転によって、
前記遊星レバー規制面（３０ａ）が前記第１モード位置で、前記第１遊星ギヤ（２３）と前記第１モードギヤ（２５）とが噛合し、前記第２遊星レバー（２８）の前記第２遊星レバーカム端（２８ａ）が前記遊星レバー規制面（３０ａ）に当接して規制されて前記第２遊星ギヤ（２７）と前記第２モードギヤ（２９）とが離脱し（図７）、
前記遊星レバー規制面（３０ａ）が前記第２モード位置で、前記第１遊星レバー（２４）の前記第１遊星レバーカム端（２４ａ）が前記遊星レバー規制面（３０ａ）に当接して規制されて前記第１遊星ギヤ（２３）と前記第１モードギヤ（２５）とが離脱し、前記第２遊星ギヤ（２７）と前記第２モードギヤ（２９）とが噛合し（図８）、
前記遊星レバー規制面（３０ａ）が前記第３モード位置で、前記第１遊星ギヤ（２３）と前記第１モードギヤ（２５）とが噛合し、前記第２遊星ギヤ（２７）と前記第２モードギヤ（２９）とが噛合する（図９）ことを特徴とする駆動装置である。 The present invention relates to a drive device that transmits power from a drive source to one or both of the first and second mode gears (25, 29).
The drive source includes a motor (21) capable of rotating in the forward and reverse directions, a motor gear provided on a rotating shaft of the motor (21), and a reduction gear (32) rotated by the motor gear,
A first sun gear (22) meshing with the reduction gear (32);
A first planetary gear (23) meshed with the first sun gear (22), meshed with the first mode gear (25), and disengaged;
A first planetary lever (24), which is rotatably provided on an axis of the first sun gear (22), and at one end thereof, the first planetary gear (23) is rotatably provided, and the other A first planetary lever (24) having a first planetary lever cam end (24a) at the end;
A second sun gear (26) meshing with the reduction gear (32);
A second planetary gear (27) meshing with the second sun gear (26), meshing with and disengaging from the second mode gear (29);
A second planetary lever (28), which is rotatably provided on an axis of the second sun gear (22), wherein the second planetary gear (27) is rotatably provided at one end; A second planetary lever (28) having a second planetary lever cam end (28a) at the end;
A rotatable cam gear (30) having a planetary lever restricting surface (30a) on one surface side and an inner wall surface having a missing portion in the circumferential direction on the other surface side and facing the groove. A cam gear (30) having an abutting surface (30c),
A cam switching gear (34) that can be engaged and disengaged with the first planetary gear (23), and can be engaged and disengaged with the cam gear (30);
A cam switching lever (33), wherein the cam switching gear (34) is rotatably provided at one end, and the cam gear (30) is radially inward from the missing portion at the other end. The cam switching lever (33) having a hooking portion (33a) displaceable outward;
A return spring (35), wherein the hooking portion (33a) applies a spring force directed inward in the radial direction of the cam gear (30) to the cam switching lever (33);
As the motor (21) rotates in one direction (counterclockwise), the first planetary gear (23) meshes with the cam switching gear (34), and the hooking portion (33a) resists the spring force. The cam switching gear (34) meshes with the cam gear (30), and the hooking portion (33a) is in the radial direction against the spring force at the missing portion. And the cam switching gear (34) is disengaged from the cam gear (30) (FIGS. 4 and 5),
Due to the other direction (clockwise) rotation of the motor (21), the first planetary gear (23) is disengaged from the cam switching gear (34), and the hooking portion (33a) is moved from the missing portion to the spring. A return spring (35) that allows the cam gear (30) to enter inward in the radial direction by force (FIG. 6);
The planetary lever restricting surface (30a) of the cam gear (30) is first to third from the missing portion in order in the rotational direction of the cam gear (30) rotated by the one-way rotation of the motor (21). Has a mode position,
By the other direction rotation of the motor (21),
When the planetary lever restricting surface (30a) is in the first mode position, the first planetary gear (23) and the first mode gear (25) mesh with each other, and the second planetary lever (28) has the second planetary gear. The lever cam end (28a) abuts on the planetary lever regulating surface (30a) and is regulated, and the second planetary gear (27) and the second mode gear (29) are separated (FIG. 7).
The planetary lever restricting surface (30a) is in the second mode position, and the first planetary lever cam end (24a) of the first planetary lever (24) is in contact with the planetary lever restricting surface (30a) to be restricted. The first planetary gear (23) and the first mode gear (25) are disengaged, and the second planetary gear (27) and the second mode gear (29) are engaged with each other (FIG. 8).
When the planetary lever restricting surface (30a) is in the third mode position, the first planetary gear (23) and the first mode gear (25) are meshed, and the second planetary gear (27) and the second mode gear are engaged. (29) meshes with the driving device (FIG. 9) .

本発明に従えば、モータ２１の一方向（反時計方向）回転によって、
第１遊星ギヤ２３がカム切替ギヤ３４、カム切替レバー３３、引掛部３３ａを、復帰スプリング３４のばね力に抗して押して、引掛部３３ａが当接面３０ｃに当接しており（図３）、
カム切替ギヤ３４がカムギヤ３０に噛合して回転し、
引掛部３３ａが、当接面３０ｃの欠落部分から、カムギヤ３０の径方向内方から外方に変位すると、第１遊星ギヤ２３がカム切替ギヤ３４を、復帰スプリング３５のばね力に抗して、押すことによって、カム切替ギヤ３４がカムギヤ３０から離脱し（図４、図５）、
次に、モータ２１の他方向（時計方向）回転によって、第１遊星ギヤ２３がカム切替ギヤ３４から離脱してカム切替ギヤ３４を押さなくなり、カム切替レバー３３の引掛部３３ａを、前記欠落部分から、復帰スプリング３５のばね力によって、カムギヤ３０の径方向の内方に入り込ませ（図６）、
その後、モータ２１の一方向（反時計方向）回転によって、カムギヤ３０の遊星レバー規制面３０ａを第１〜第３モード位置に順にもたらし、
第１〜第３の各モード位置に設定した状態で、
モータ２１を他方（時計方向）回転して第１遊星レバー２４の第１遊星レバーカム端２４ａと、第２遊星レバー２８の第２遊星レバーカム端２８ａとを選択的に規制して、駆動源のモータ２１の動力を、第１および第２モードギヤ２５，２９のいずれか一方（図７または図８）および両者（図９）に伝達する。 According to the present invention, by rotating the motor 21 in one direction (counterclockwise),
The first planetary gear 23 pushes the cam switching gear 34, the cam switching lever 33, and the hooking portion 33a against the spring force of the return spring 34, and the hooking portion 33a is in contact with the contact surface 30c (FIG. 3). ,
The cam switching gear 34 meshes with the cam gear 30 and rotates.
When the hook portion 33a is displaced from the missing portion of the contact surface 30c from the radially inner side to the outer side of the cam gear 30, the first planetary gear 23 resists the cam switching gear 34 against the spring force of the return spring 35. By pushing, the cam switching gear 34 is detached from the cam gear 30 (FIGS. 4 and 5),
Next, when the motor 21 rotates in the other direction (clockwise), the first planetary gear 23 is disengaged from the cam switching gear 34 and does not press the cam switching gear 34, and the hooking portion 33 a of the cam switching lever 33 is moved away from the missing portion. From the inside of the cam gear 30 in the radial direction by the spring force of the return spring 35 (FIG. 6),
Thereafter, by rotating the motor 21 in one direction (counterclockwise), the planetary lever restricting surface 30a of the cam gear 30 is sequentially brought to the first to third mode positions,
With the first to third mode positions set,
The motor 21 is rotated in the other direction (clockwise) to selectively restrict the first planetary lever cam end 24a of the first planetary lever 24 and the second planetary lever cam end 28a of the second planetary lever 28, and the motor of the drive source 21 is transmitted to one of the first and second mode gears 25 and 29 (FIG. 7 or FIG. 8) and both (FIG. 9).

本発明によれば、１つのモータ２１を駆動源として、第１および第２モードギヤ２５，２９のいずれか一方および両者に回転駆動力を伝達する際に、図５の基本状態から図６の状態に復帰させる復帰スプリング３５を設けるので、基本状態にあることを確認するスイッチなどを設ける必要はなく、機構を簡略化することができる。 According to the present invention, when the rotational driving force is transmitted to one or both of the first and second mode gears 25 and 29 using one motor 21 as a drive source, the state shown in FIG. Since the return spring 35 for returning to the position is provided, there is no need to provide a switch for confirming the basic state, and the mechanism can be simplified.

図１は、本発明の実施の一形態としての駆動装置２０の概略的な構成を示す。駆動装置２０は、駆動源として一つのモータ２１を含む。モータ２１の駆動力は、受信側の太陽ギヤ２２を介して受信側遊星ギヤ２３に伝達される。受信側遊星ギヤ２３は、受信側遊星レバー２４の一方端部に軸支される。受信側遊星ギヤ２３は、受信モードで、駆動力を受信側減速ギヤ２５へ伝達する。受信側減速ギヤ２５から先は、図示を省略している受信用ローラ類へと駆動力が伝達される。また、モータ２１の駆動力は、送信側の太陽ギヤ２６を介して、送信側遊星ギヤ２７に伝達される。送信側遊星ギヤ２７は、送信側遊星レバー２８の一方端部に軸支される。送信側遊星ギヤ２８は、送信モードで、駆動力を送信側減速ギヤ２９へ伝達する。送信側減速ギヤ２９から先は、図示を省略している送信用ローラ類へと駆動力が伝達される。 FIG. 1 shows a schematic configuration of a drive device 20 as an embodiment of the present invention. The drive device 20 includes one motor 21 as a drive source. The driving force of the motor 21 is transmitted to the receiving planetary gear 23 via the receiving sun gear 22. The receiving planetary gear 23 is pivotally supported at one end of the receiving planetary lever 24. The reception-side planetary gear 23 transmits driving force to the reception-side reduction gear 25 in the reception mode. A driving force is transmitted from the receiving reduction gear 25 to the receiving rollers not shown. Further, the driving force of the motor 21 is transmitted to the transmitting planetary gear 27 via the transmitting sun gear 26. The transmission-side planetary gear 27 is pivotally supported at one end of the transmission-side planetary lever 28. The transmission-side planetary gear 28 transmits driving force to the transmission-side reduction gear 29 in the transmission mode. From the transmission side reduction gear 29, the driving force is transmitted to the transmission rollers not shown.

受信側遊星レバー２４および送信側遊星レバー２８の一方端部と他方端部との中間部分は、太陽ギヤ２２，２６の回転軸を支点として、それぞれ揺動変位が可能である。受信側遊星レバー２４が揺動変位すると、受信側遊星ギヤ２３は、太陽ギヤ２２と噛合する状態を保ちながら、受信側減速ギヤ２５と噛合する位置と、カム切替ギヤ３４と噛合する位置との間を移動する。送信側遊星レバー２８が揺動変位すると送信側遊星ギヤ２７は、太陽ギヤ２６と噛合する状態を保ちながら、送信側減速ギヤ２９と噛合する位置と、噛合しない位置との間を移動する。カムギヤ３０に関しては、カムスプリング３１が設けられる。モータ２１の回転軸に設けられるモータギヤと噛合し、太陽ギヤ２２，２６に回転駆動力を伝達するために、減速ギヤ３２が設けられる。駆動力の発生源であるモータ２１が図の反時計回り方向に回動すると、受信側遊星レバー２４が反時計回り方向に揺動変位し、受信側遊星レバー２４の一方端部に軸支されている受信側遊星ギヤ２３がカム切替ギヤ３４へ噛合し、さらにカム切替ギヤ３４がカムギヤ３０に噛合し、カムギヤ３０は時計回り方向に回転する。
このような構成は、基本的に、図１０〜図１４に示す駆動機構と同様である。 The intermediate portion between one end and the other end of the receiving planetary lever 24 and the transmitting planetary lever 28 can be oscillated and displaced with the rotation shafts of the sun gears 22 and 26 as fulcrums. When the receiving planetary lever 24 swings and displaces, the receiving planetary gear 23 maintains a state in which the receiving planetary gear 23 is engaged with the sun gear 22, and a position that engages with the receiving reduction gear 25 and a position that engages with the cam switching gear 34. Move between. When the transmission-side planetary lever 28 is oscillated and displaced, the transmission-side planetary gear 27 moves between a position where the transmission-side planetary gear 27 meshes with the transmission-side reduction gear 29 and a position where the transmission-side planetary gear 27 does not mesh. For the cam gear 30, a cam spring 31 is provided. A reduction gear 32 is provided to mesh with a motor gear provided on the rotation shaft of the motor 21 and transmit a rotational driving force to the sun gears 22 and 26. When the motor 21 that is the driving force generation source rotates counterclockwise in the figure, the receiving planetary lever 24 swings and displaces counterclockwise and is pivotally supported by one end of the receiving planetary lever 24. The receiving planetary gear 23 is engaged with the cam switching gear 34, the cam switching gear 34 is further engaged with the cam gear 30, and the cam gear 30 rotates in the clockwise direction.
Such a configuration is basically the same as the drive mechanism shown in FIGS.

本実施形態の駆動機構２０は、カムスプリング３１を利用して、カムギヤ３０が基本状態（後述の図５参照）に復帰するように付勢する。また、切替を確実に行うために、カム切替レバー３３およびカム切替ギヤ３４が設けられる。カム切替レバー３３は、切替レバー復帰スプリング３５で、カムギヤ３０に接近するように付勢される。 The drive mechanism 20 of this embodiment uses a cam spring 31 to urge the cam gear 30 to return to a basic state (see FIG. 5 described later) . Further, a cam switching lever 33 and a cam switching gear 34 are provided in order to perform switching reliably. The cam switching lever 33 is biased by the switching lever return spring 35 so as to approach the cam gear 30.

図２は、図１のカム切替レバー３３周辺を詳細に示す。図２（ａ）は背面視、図２（ｂ）は図２（ａ）の切断面線Ａ−Ａからの側面断面視、図２（ｃ）は正面視してそれぞれ示す。カムギヤ３０は、正面側に遊星レバー規制面３０ａおよびカムスプリング当接面３０ｂを有する。カムギヤ３０の背面側には、カム切替レバー当接面３０ｃおよびカム切替レバー押上面３０ｄを有する。カム切替レバー３３は、一端側にカムギヤ引掛部３３ａを有し、他端側にはカム切替ギヤ３４が軸支される。カム切替ギヤ３４は、カムギヤ３０と噛合することがある。カム切替ギヤ３４は、受信側遊星ギヤ２３と噛合することもある。カムギヤ引掛部３３ａは、正面側に突出する。カム切替レバー当接面３０ｃは、カムギヤ３０の背面側の表面に、円周方向に形成される溝に臨む内壁面として形成される。カム切替レバー当接面３０ｃは、カム切替レバー押上面３０ｄが形成されている部分の周辺で欠落して途切れており、カム切替レバー当接面３０ｃが臨む円周方向の溝は、この欠落部分で径方向の外方に連通している。 FIG. 2 shows the periphery of the cam switching lever 33 in FIG. 1 in detail. 2 (a) is a rear view, FIG. 2 (b) is a side sectional view from the cutting plane line AA of FIG. 2 (a), and FIG. 2 (c) is a front view. The cam gear 30 has a planetary lever restriction surface 30a and a cam spring contact surface 30b on the front side. On the back side of the cam gear 30, a cam switching lever contact surface 30c and a cam switching lever pushing surface 30d are provided. The cam switching lever 33 has a cam gear hooking portion 33a on one end side, and a cam switching gear 34 is pivotally supported on the other end side. The cam switching gear 34 may mesh with the cam gear 30. The cam switching gear 34 may mesh with the receiving planetary gear 23. The cam gear hooking portion 33a protrudes to the front side. The cam switching lever contact surface 30 c is formed on the surface on the back side of the cam gear 30 as an inner wall surface facing a groove formed in the circumferential direction. The cam switching lever abutting surface 30c is missing and interrupted around the portion where the cam switching lever pressing surface 30d is formed, and the circumferential groove facing the cam switching lever abutting surface 30c is the missing portion. And communicates radially outward.

図３は、カム切替レバー３３のカムギヤ引掛部３３ａがカムギヤ３０のカム切替レバー当接面３０ｃに当接している状態を示す。このように、カムギヤ引掛部３３ａがカムギヤ３０のカム切替レバー当接面３０ｃに当接してカム切替レバー３３の下方への移動が規制されている場合、カム切替ギヤ３４はカムギヤ３０と噛合している。モータ２１を反時計回り方向に回転させると受信側の太陽ギヤ２２は反時計回り方向に回転する。駆動力は、受信側遊星ギヤ２３からカム切替ギヤ３４を介してカムギヤ３０に伝達されて、カムギヤ３０は時計回り方向に回転する。カムギヤ引掛部３３ａがカムギヤ当接面３０ｃに当接してカム切替レバー３３が下方への移動を規制されている限り、カム切替ギヤ３４とカムギヤ３０の噛合は維持される。 FIG. 3 shows a state where the cam gear hooking portion 33 a of the cam switching lever 33 is in contact with the cam switching lever contact surface 30 c of the cam gear 30. As described above, when the cam gear hooking portion 33 a contacts the cam switching lever contact surface 30 c of the cam gear 30 and the downward movement of the cam switching lever 33 is restricted, the cam switching gear 34 meshes with the cam gear 30. Yes. When the motor 21 is rotated counterclockwise, the receiving-side sun gear 22 rotates counterclockwise. The driving force is transmitted from the receiving planetary gear 23 to the cam gear 30 via the cam switching gear 34, and the cam gear 30 rotates in the clockwise direction. As long as the cam gear hooking portion 33a contacts the cam gear contact surface 30c and the cam switching lever 33 is restricted from moving downward, the engagement of the cam switching gear 34 and the cam gear 30 is maintained.

図４は、カム切替レバー３３のカムギヤ引掛部３３ａがカム切替レバー当接面３０ｃの欠落部から径方向の外方に離脱している状態を示す。図３に示す状態から、そのまま、モータ２１を回転させ続けると、カム切替レバー３３のカムギヤ引掛部３３ａはカムギヤ３０のカム切替レバー当接面３０ｃから外れ、カム切替レバー３３の下方への規制はなくなり、受信側遊星ギヤ２３に押されて下方へ移動する。このとき、カム切替レバー３３が下方へ移動することによって、カム切替ギヤ３４とカムギヤ３０との噛合も外れ、カムギヤ３０の回転は停止する。すなわち、モータ２１を十分長い時間反時計回り方向に回転させると、カムギヤ３０とカム切替ギヤ３４との噛合が外れるまでカムギヤ３０は回転を続け、噛合が外れると回転を停止するので、モータ２１の回転時間にかかわらずカムギヤ３０の回転位置を、図示の状態とすることができる。 FIG. 4 shows a state where the cam gear hooking portion 33a of the cam switching lever 33 is detached radially outward from the missing portion of the cam switching lever contact surface 30c. If the motor 21 is continuously rotated from the state shown in FIG. 3, the cam gear hooking portion 33a of the cam switching lever 33 is disengaged from the cam switching lever contact surface 30c of the cam gear 30, and the cam switching lever 33 is restricted downward. It is pushed by the receiving planetary gear 23 and moves downward. At this time, when the cam switching lever 33 moves downward, the cam switching gear 34 and the cam gear 30 are disengaged, and the rotation of the cam gear 30 stops. That is, if the motor 21 is rotated counterclockwise for a sufficiently long time, the cam gear 30 continues to rotate until the meshing between the cam gear 30 and the cam switching gear 34 is disengaged, and the rotation is stopped when the meshing is disengaged. Regardless of the rotation time, the rotational position of the cam gear 30 can be in the illustrated state.

この十分長い時間とは、カムギヤ３０を一回転以上させるための時間であればよく、モータ２１からカムギヤ３０までの減速比の逆数分だけモータ２１を回転し続けることで実現することができる。たとえば、減速比が０．１であれば、モータ２１を１０回転以上させれる時間があればよい。カム切替ギヤ３４とカムギヤ３０との噛合がなくなると、カムギヤ３０はすべてのギヤとの噛合がなくなりフリー状態となる。ここで、カムスプリング３１は、カムギヤ３０のカムスプリング当接面３０ｂを押すように配置されている。 This sufficiently long time may be a time for rotating the cam gear 30 one or more times, and can be realized by continuing to rotate the motor 21 by the reciprocal of the reduction ratio from the motor 21 to the cam gear 30. For example, if the reduction ratio is 0.1, it is sufficient if there is time for the motor 21 to be rotated 10 times or more. When the engagement of the cam switching gear 34 and the cam gear 30 is lost, the cam gear 30 is not engaged with all the gears and becomes free. Here, the cam spring 31 is disposed so as to push the cam spring contact surface 30 b of the cam gear 30.

図５は、フリーな状態となるカムギヤ３０が、カムスプリング３１によってカムスプリング当接面３０ｂを押され、図４の状態から時計回り方向に角変位した状態を示す。カムスプリング３１は、大略的にＶ字状であり、一辺側がカムスプリング当接面３０ｂに当接し、他辺側が駆動装置のフレームに固定される。このために、一辺側と他辺側との間の角度が小さくなると、ばね反力として角度を大きくする方向に一辺側を押す。図５の状態では、一辺側が直線状に延びる方向とカムスプリング当接面３０ｂの表面とが一致する。このときのカムスプリング当接面３０ｂのカムギヤ３０の中心からの半径は、最も小さい状態となる。このようなカムギヤ３０の角度の状態は基本状態となる。 FIG. 5 shows a state in which the cam gear 30 in a free state is angularly displaced in the clockwise direction from the state of FIG. 4 when the cam spring contact surface 30b is pushed by the cam spring 31. The cam spring 31 is generally V-shaped, one side abuts against the cam spring abutment surface 30b, and the other side is fixed to the frame of the drive device. For this reason, when the angle between the one side and the other side decreases, the one side is pushed in the direction of increasing the angle as a spring reaction force. In the state of FIG. 5, the direction in which the one side extends linearly coincides with the surface of the cam spring contact surface 30 b. At this time, the radius of the cam spring contact surface 30b from the center of the cam gear 30 is the smallest. Such an angle state of the cam gear 30 is a basic state.

以上のように、ファクシミリや複写機など、一つのモータ２１で複数のローラ類を個別に駆動する切替機構を有する装置において、駆動力の切替を制御するためにカムと遊星レバーを利用する駆動装置２０に、カム切替レバー３３およびそれを復帰させるためのカム切替スプリング３５を付加することによって、カムの回転位置を検出するためのカムセンサを廃止することを実現する駆動装置２０とすることができる。また、カム切替レバー３３がカムギヤ３０から外れた後、振動その他外乱などによって、カムギヤ３０の回転位置が移動してしまうのを防止するためのカムスプリング３１をカムギヤ３０の回転力に利用することができる。 As described above, in a device having a switching mechanism for individually driving a plurality of rollers by a single motor 21 such as a facsimile or a copying machine, a driving device that uses a cam and a planetary lever to control switching of driving force By adding a cam switching lever 33 and a cam switching spring 35 for returning the cam switching lever 33 to the cam 20, a driving device 20 that realizes the elimination of the cam sensor for detecting the rotational position of the cam can be obtained. Further, the cam spring 31 for preventing the rotational position of the cam gear 30 from moving due to vibration or other disturbance after the cam switching lever 33 is disengaged from the cam gear 30 can be used as the rotational force of the cam gear 30. it can.

さらに、カム切替レバー３３が復帰する際に、振動その他外乱などによって、カムギヤ３０の回転位置が移動してしまうのを防止するためのカムスプリング３１の機能を一時的に無効にするため、カムスプリング３１がカムギヤ３０に当接するカムスプリング当接面３０ｂのフラット部分を部分的に曲面とすることが好ましい。 Furthermore, in order to temporarily disable the function of the cam spring 31 for preventing the rotational position of the cam gear 30 from moving due to vibration or other disturbances when the cam switching lever 33 is returned, the cam spring It is preferable that the flat part of the cam spring contact surface 30b where 31 contacts the cam gear 30 is partially curved.

図６は、図５に示す基本状態から、モータ２１を時計回り方向に回転させた状態を示す。モータ２１の回転によって、受信側遊星レバー２４は時計回り方向へ揺動変位し、図６の上方へのばね力を発揮する切替レバー復帰スプリング３５の伸長とともに、カム切替レバー３３は上方へ移動する。このとき、カム切替レバー３３のカムギヤ引掛部３３ａは、カムギヤ３０の前記欠落部分から径方向の内方に変位してカム切替レバー押上面３０ｄを押して、カムギヤ３０をさらに時計回り方向に角変位させる。 FIG. 6 shows a state in which the motor 21 is rotated clockwise from the basic state shown in FIG. As the motor 21 rotates, the receiving planetary lever 24 swings and displaces in the clockwise direction, and the cam switching lever 33 moves upward along with the extension of the switching lever return spring 35 that exerts the upward spring force in FIG. . At this time, the cam gear hook portion 33a of the cam switching lever 33, by pushing the cam switching lever push-up face 30d are displaced inwardly from the missing portion of the cam gear 30 in the radial direction, further angular displacement in a clockwise direction the cam gear 30 .

本来、カムスプリング３１は、振動その他外乱等によってカムギヤ３０が回転してしまうのを防ぐためにある。ここでのカムギヤ３０の角変位の範囲においては、カムスプリング３１とカムギヤ３０のカムスプリング当接面３０ｂは最も半径の小さい部分で当接しており、カムスプリング３１は最も開いた状態、すなわちカムギヤ３０のカムスプリング当接面３０ｂを押す荷重が最も少なく、しかも一定となるようになっているので、カム切替レバー押上面３０ｄがカムギヤ３０を回転させる力を阻害しないように設定されている。したがって、カム切替レバー３３が復帰する際、切替レバー復帰スプリング３５の復帰力をカムギヤ３０の回転力に利用することができる。 Originally, the cam spring 31 is for preventing the cam gear 30 from rotating due to vibration or other disturbances. In this range of angular displacement of the cam gear 30, the cam spring 31 and the cam spring contact surface 30b of the cam gear 30 are in contact with each other at the smallest radius, and the cam spring 31 is in the most open state, that is, the cam gear 30. Since the load that pushes the cam spring abutting surface 30b is the smallest and constant, the cam switching lever pushing surface 30d is set so as not to impede the force for rotating the cam gear 30. Accordingly, when the cam switching lever 3 3 returns, it is possible to utilize the restoring force of the switching lever return spring 35 to the rotational force of the cam gear 30.

受信側遊星レバー２４が図６に示す位置になるまでモータ２１を時計回り方向に回転させると、カムギヤ３０も図６の位置まで角変位する。さらにこのときには、カム切替レバー３３のカムギヤ引掛部３３ａは、切替レバー復帰スプリング３５のばね力によってカムギヤ３０のカム切替レバー当接面３０ｃの内側に入っているので、次にモータ２１を反時計回り方向に回転させるときには、受信側遊星ギヤ２３がカム切替ギヤ３４を切替レバー復帰スプリング３５のばね力に抗して図６の下方に押して、カム切替レバー３３のカムギヤ引掛部３３ａがカム切替レバー当接面３０ｃに当接することによって、カム切替レバー３３の下方への移動は規制され、カム切替ギヤ３４とカムギヤ３０の噛合は外れることなく、カムギヤ３０は図６の時計方向に回転する。 When the motor 21 is rotated clockwise until the receiving planetary lever 24 reaches the position shown in FIG. 6, the cam gear 30 is also angularly displaced to the position shown in FIG. Further, at this time, the cam gear hooking portion 33a of the cam switching lever 33 is located inside the cam switching lever contact surface 30c of the cam gear 30 by the spring force of the switching lever return spring 35. When rotating in the direction, the receiving planetary gear 23 pushes the cam switching gear 34 downward in FIG. 6 against the spring force of the switching lever return spring 35, so that the cam gear hooking portion 33a of the cam switching lever 33 is pushed by the cam switching lever. By contacting the contact surface 30c, the downward movement of the cam switching lever 33 is restricted, and the cam gear 30 rotates clockwise in FIG. 6 without disengaging the cam switching gear 34 and the cam gear 30.

以上で説明している一連の動作、すなわち、モータ２１を十分長い時間反時計回り方向に回転後、モータ２１を一定量時計回り方向に回転させることで、カムギヤ３０を図６に示す位置に回転させることができ、カムギヤ３０の図６における時計方向の回転によって順に、前記欠落部分から、さらに図１０〜図１４に示す従来技術にモータ２１の回動量を制御することによって、送信・受信・コピーの各モードの位置に応じたカムモードを実現することができる。しかも図１０〜図１３のようなカムスイッチ１２は不要となるので、一つのモータ２１を駆動源として、駆動力の伝達経路を切替え可能にし、しかも機構を簡略化することができる。 The series of operations described above, that is, after rotating the motor 21 counterclockwise for a sufficiently long time, the motor 21 is rotated clockwise by a certain amount, whereby the cam gear 30 is rotated to the position shown in FIG. By sequentially rotating the cam gear 30 in the clockwise direction in FIG. 6, the amount of rotation of the motor 21 is further controlled from the missing portion according to the prior art shown in FIGS. 10 to 14. The cam mode corresponding to the position of each mode can be realized. In addition, since the cam switch 12 as shown in FIGS. 10 to 13 is not required, it is possible to switch the transmission path of the driving force using one motor 21 as a driving source, and to simplify the mechanism.

図７は、カムギヤ３０が受信モードに対応する角度となる状態を示す。カムギヤ３０を受信モードの状態にして、モータ２１を時計回り方向に回転させると、減速ギヤ３２は反時計回り方向に回転し、受信側の太陽ギヤ２２は時計回り方向に回転する。受信側遊星レバー２３も時計回り方向に揺動変位し、受信側遊星ギヤ２３が受信側減速ギヤ２５へ噛合し、受信側の各部に駆動力が伝達される。減速ギヤ３２は送信側の太陽ギヤ２６とも噛合しているので、太陽ギヤ２６も時計回り方向に回転し、送信側遊星レバー２８を時計回り方向に揺動変位させようとする。しかし、送信側遊星レバーカム側端２８ａがカムギヤ３０の遊星レバー規制面３０ａに当接して送信側遊星レバー２８の揺動変位を規制し、送信側減速ギヤ２９へは駆動力が伝わらない。 FIG. 7 shows a state where the cam gear 30 has an angle corresponding to the reception mode. When the cam gear 30 is set in the reception mode and the motor 21 is rotated in the clockwise direction, the reduction gear 32 is rotated in the counterclockwise direction, and the receiving-side sun gear 22 is rotated in the clockwise direction. The receiving-side planetary lever 23 is also oscillated and displaced in the clockwise direction, the receiving-side planetary gear 23 is engaged with the receiving-side reduction gear 25, and the driving force is transmitted to each part on the receiving side. Since the reduction gear 32 is also engaged with the transmission-side sun gear 26, the sun gear 26 also rotates in the clockwise direction, and tries to swing and displace the transmission-side planetary lever 28 in the clockwise direction. However, the transmission-side planetary lever cam side end 28 a abuts on the planetary lever regulating surface 30 a of the cam gear 30 to regulate the swing displacement of the transmission-side planetary lever 28, and no driving force is transmitted to the transmission-side reduction gear 29.

図８は、カムギヤ３０が送信モードに対応する角度となる状態を示す。モータ２１を時計回り方向に回転させると、減速ギヤ３２は反時計回り方向に回転し、受信側の太陽ギヤ２２は時計回り方向に回転する。受信側遊星レバー２４が時計回り方向に揺動変位し、受信側遊星ギヤ２３が受信側減速ギヤ２５へ噛合しようとする。しかし、受信側遊星レバーカム側端２４ａがカムギヤ３０の遊星レバー規制面３０ａに当接して、受信側遊星レバー２４の回転を規制し、受信側減速ギヤ２５へは駆動力が伝わらない。一方、送信側遊星レバーカム側端２８ａはカムギヤ３０の遊星レバー規制面３０ａには当接しないため、送信側遊星レバー２８の揺動変位は規制されず、送信側遊星ギヤ２７が送信側減速ギヤ２９に噛合し、送信側減速ギヤ２９へ駆動力が伝達される。 FIG. 8 shows a state in which the cam gear 30 has an angle corresponding to the transmission mode. When the motor 21 is rotated in the clockwise direction, the reduction gear 32 rotates in the counterclockwise direction, and the receiving-side sun gear 22 rotates in the clockwise direction. The receiving planetary lever 24 swings and displaces in the clockwise direction, and the receiving planetary gear 23 attempts to mesh with the receiving reduction gear 25. However, the receiving planetary lever cam side end 24 a comes into contact with the planetary lever restricting surface 30 a of the cam gear 30 to restrict the rotation of the receiving planetary lever 24, and no driving force is transmitted to the receiving reduction gear 25. On the other hand, the transmitting planetary lever cam side end 28a does not contact the planetary lever restricting surface 30a of the cam gear 30, so that the swinging displacement of the transmitting planetary lever 28 is not restricted, and the transmitting planetary gear 27 is connected to the transmitting side reduction gear 29. And the driving force is transmitted to the transmission side reduction gear 29.

図９は、カムギヤ３０がコピーモードに対応する角度となる状態を示す。モータ２１を時計回り方向に回転させると、減速ギヤ３２は反時計回り方向に回転し、受信側の太陽ギヤ２２は時計回り方向に回転する。受信側遊星レバー２４も時計回り方向に揺動変位する。受信側遊星レバーカム側端２４ａは、カムギヤ３０の遊星レバー規制面３０ａには当接しないため、受信側遊星レバー２４の揺動変位は規制されず、受信側遊星ギヤ２３が受信側減速ギヤ２５に噛合し、受信側減速ギヤ２５へ駆動力が伝達される。一方、減速ギヤ３２から駆動力が伝達される送信側の太陽ギヤ２６は時計回り方向に回転し、送信側遊星レバー２８も時計回り方向に揺動変位する。送信側遊星レバーカム側端２８ａは、カムギヤ３０の遊星レバー規制面３０ａには当接しないため、送信側遊星レバー２８の揺動変位は規制されず、送信側遊星ギヤ２７が送信側減速ギヤ２９に噛合し、送信側減速ギヤ２９へ駆動力が伝達される。 FIG. 9 shows a state where the cam gear 30 is at an angle corresponding to the copy mode. When the motor 21 is rotated in the clockwise direction, the reduction gear 32 rotates in the counterclockwise direction, and the receiving-side sun gear 22 rotates in the clockwise direction. The receiving planetary lever 24 is also oscillated and displaced in the clockwise direction. Since the receiving planetary lever cam side end 24 a does not contact the planetary lever regulating surface 30 a of the cam gear 30, the swinging displacement of the receiving planetary lever 24 is not regulated, and the receiving planetary gear 23 becomes the receiving side reduction gear 25. The drive force is transmitted to the receiving side reduction gear 25. On the other hand, the transmission-side sun gear 26 to which the driving force is transmitted from the reduction gear 32 rotates in the clockwise direction, and the transmission-side planetary lever 28 also swings and displaces in the clockwise direction. Since the transmission side planetary lever cam side end 28 a does not contact the planetary lever restriction surface 30 a of the cam gear 30, the swinging displacement of the transmission side planetary lever 28 is not restricted, and the transmission side planetary gear 27 becomes the transmission side reduction gear 29. Engage and the driving force is transmitted to the transmission side reduction gear 29.

なお、以上で説明している駆動装置２０は、ファクシミリ装置に使用することを想定しているけれども、複数の動作を駆動力の伝達経路で切替える機能を必要とする装置であれば、ファクシミリ装置以外の装置に使用することもできる。 Although the driving device 20 described above is assumed to be used for a facsimile machine, any device other than a facsimile machine may be used as long as it requires a function for switching a plurality of operations by a driving force transmission path. It can also be used for other devices.

本発明の実施の一形態としての駆動装置２０の概略的な構成を示す簡略化した正面図である。It is the simplified front view which shows the schematic structure of the drive device 20 as one Embodiment of this invention. 図１のカム切替レバー３３周辺を詳細に示す部分的な背面図、側面断面図および正面図である。FIG. 2 is a partial rear view, a side sectional view, and a front view showing in detail the periphery of a cam switching lever 33 in FIG. 1. 図１の駆動装置２０で、カム切替レバー３３のカムギヤ引掛部３３ａがカムギヤ３０のカム切替レバー当接面３０ｃに当接している状態を示す簡略化した正面図である。2 is a simplified front view showing a state in which the cam gear hooking portion 33a of the cam switching lever 33 is in contact with the cam switching lever contact surface 30c of the cam gear 30 in the drive device 20 of FIG. 図１の駆動装置２０で、カム切替レバー３３のカムギヤ引掛部３３ａがカム切替レバー当接面３０ｃの欠落部分から離脱している状態を示す簡略化した正面図である。FIG. 3 is a simplified front view showing a state in which the cam gear hooking portion 33a of the cam switching lever 33 is detached from the missing portion of the cam switching lever contact surface 30c in the drive device 20 of FIG. 図１の駆動装置２０で、フリーな状態となるカムギヤ３０がカムスプリング３１によって押されて基本状態となることを示す簡略化した正面図である。FIG. 2 is a simplified front view showing that a cam gear 30 that is in a free state is pushed by a cam spring 31 to a basic state in the drive device 20 of FIG. 1. 図５に示す基本状態から、モータ２１を時計回り方向に回転させた状態を示す簡略化した正面図である。It is the simplified front view which shows the state which rotated the motor 21 clockwise from the basic state shown in FIG. 図１の駆動装置２０で、カムギヤ３０が受信モードに対応する角度となる状態を示す簡略化した正面図である。FIG. 2 is a simplified front view showing a state in which the cam gear 30 is at an angle corresponding to a reception mode in the drive device 20 of FIG. 1. 図１の駆動装置２０で、カムギヤ３０が送信モードに対応する角度となる状態を示す簡略化した正面図である。FIG. 2 is a simplified front view showing a state in which the cam gear 30 is at an angle corresponding to a transmission mode in the drive device 20 of FIG. 1. 図１の駆動装置２０で、カムギヤ３０がコピーモードに対応する角度となる状態を示す簡略化した正面図である。FIG. 2 is a simplified front view showing a state in which the cam gear 30 is at an angle corresponding to a copy mode in the drive device 20 of FIG. 1. 特許文献１に開示されている考え方を適用する駆動装置の概略的な構成を示す簡略化した正面図である。It is the simplified front view which shows the schematic structure of the drive device to which the idea currently disclosed by patent document 1 is applied. 図１０のカムギヤ１０の形状を示す正面図および側面図である。It is the front view and side view which show the shape of the cam gear 10 of FIG. 図１０で、カムギヤ１０が受信モードに対応する角度となる状態を示す簡略化した正面図である。In FIG. 10, it is the simplified front view which shows the state in which the cam gear 10 becomes an angle corresponding to reception mode. 図１０で、カムギヤ１０が送信モードに対応する角度となる状態を示す簡略化した正面図である。In FIG. 10, it is the simplified front view which shows the state in which the cam gear 10 becomes the angle corresponding to transmission mode. 図１０で、カムギヤ１０がコピーモードに対応する角度となる状態を示す簡略化した正面図である。FIG. 11 is a simplified front view showing a state where the cam gear 10 is at an angle corresponding to the copy mode in FIG. 10.

Explanation of symbols

２１モータ
２２受信側太陽ギヤ
２３受信側遊星ギヤ
２４受信側遊星レバー
２４ａ受信側遊星レバーカム側端
２５受信側減速ギヤ
２６送信側太陽ギヤ
２７送信側遊星ギヤ
２８送信側遊星レバー
２８ａ送信側遊星レバーカム側端
２９送信側減速ギヤ
３０カムギヤ
３０ａ遊星レバー規制面
３０ｂカムスプリング当接面
３０ｃカム切替レバー当接面
３０ｄカム切替レバー押上面
３１カムスプリング
３２減速ギヤ
３３カム切替レバー
３３ａカムギヤ引掛面
３４カム切替ギヤ
３５切替レバー復帰スプリング 21 motor 22 reception side sun gear 23 reception side planetary gear 24 reception side planetary lever 24a reception side planetary lever cam side end 25 reception side reduction gear 26 transmission side sun gear 27 transmission side planetary gear 28 transmission side planetary lever 28a transmission side planetary lever cam side End 29 Transmission-side reduction gear 30 Cam gear 30a Planetary lever regulating surface 30b Cam spring contact surface 30c Cam switching lever contact surface 30d Cam switching lever pushing surface 31 Cam spring 32 Reduction gear 33 Cam switching lever 33a Cam gear hooking surface 34 Cam switching gear 35 Switching lever return spring

Claims

In the drive device that transmits the power from the drive source to one or both of the first and second mode gears (25, 29),
The drive source includes a motor (21) capable of rotating in the forward and reverse directions, a motor gear provided on a rotating shaft of the motor (21), and a reduction gear (32) rotated by the motor gear,
A first sun gear (22) meshing with the reduction gear (32);
A first planetary gear (23) meshed with the first sun gear (22), meshed with the first mode gear (25), and disengaged;
A first planetary lever (24), which is rotatably provided on an axis of the first sun gear (22), and at one end thereof, the first planetary gear (23) is rotatably provided, and the other A first planetary lever (24) having a first planetary lever cam end (24a) at the end;
A second sun gear (26) meshing with the reduction gear (32);
A second planetary gear (27) meshing with the second sun gear (26), meshing with and disengaging from the second mode gear (29);
A second planetary lever (28), which is rotatably provided on an axis of the second sun gear (22), wherein the second planetary gear (27) is rotatably provided at one end; A second planetary lever (28) having a second planetary lever cam end (28a) at the end;
A rotatable cam gear (30) having a planetary lever restricting surface (30a) on one surface side and an inner wall surface having a missing portion in the circumferential direction on the other surface side and facing the groove. A cam gear (30) having an abutting surface (30c),
A cam switching gear (34) that can be engaged and disengaged with the first planetary gear (23), and can be engaged and disengaged with the cam gear (30);
A cam switching lever (33), wherein the cam switching gear (34) is rotatably provided at one end, and the cam gear (30) is radially inward from the missing portion at the other end. The cam switching lever (33) having a hooking portion (33a) displaceable outward;
A return spring (35), wherein the hooking portion (33a) applies a spring force directed inward in the radial direction of the cam gear (30) to the cam switching lever (33);
By the one-way rotation of the motor (21), the first planetary gear (23) meshes with the cam switching gear (34), and the hooking portion (33a) resists the spring force and the contact surface. (30c), the cam switching gear (34) meshes with the cam gear (30), and the hooking portion (33a) is displaced radially outward against the spring force at the missing portion. The cam switching gear (34) is disengaged from the cam gear (30),
Due to the other direction rotation of the motor (21), the first planetary gear (23) is disengaged from the cam switching gear (34), and the hooking portion (33a) is released from the missing portion by the spring force. A return spring (35) for allowing the cam gear (30) to enter inward in the radial direction;
The planetary lever restricting surface (30a) of the cam gear (30) is first to third from the missing portion in order in the rotational direction of the cam gear (30) rotated by the one-way rotation of the motor (21). Has a mode position,
By the other direction rotation of the motor (21),
When the planetary lever restricting surface (30a) is in the first mode position, the first planetary gear (23) and the first mode gear (25) mesh with each other, and the second planetary lever (28) has the second planetary gear. The lever cam end (28a) is regulated by contacting the planetary lever regulating surface (30a), and the second planetary gear (27) and the second mode gear (29) are separated,
The planetary lever restricting surface (30a) is in the second mode position, and the first planetary lever cam end (24a) of the first planetary lever (24) is in contact with the planetary lever restricting surface (30a) to be restricted. The first planetary gear (23) and the first mode gear (25) are disengaged, and the second planetary gear (27) and the second mode gear (29) are meshed,
When the planetary lever restricting surface (30a) is in the third mode position, the first planetary gear (23) and the first mode gear (25) are meshed, and the second planetary gear (27) and the second mode gear are engaged. (29) meshes with the drive device.