JP2010164064A - Low back surface gap precision planetary type gear reducer - Google Patents

Low back surface gap precision planetary type gear reducer Download PDF

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JP2010164064A
JP2010164064A JP2009004320A JP2009004320A JP2010164064A JP 2010164064 A JP2010164064 A JP 2010164064A JP 2009004320 A JP2009004320 A JP 2009004320A JP 2009004320 A JP2009004320 A JP 2009004320A JP 2010164064 A JP2010164064 A JP 2010164064A
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planetary gear
planetary
shell
tooth section
sun gear
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Chung-Shing Jang
重興 張
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Apex Dynamics Inc
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Abstract

<P>PROBLEM TO BE SOLVED: To extend a useful life by reducing the wear quantity of a planetary gear and enabling fine adjustment of meshing after a back surface gap is created, and reducing noise and vibration by increasing meshing accuracy. <P>SOLUTION: In a gear reducer, a planetary gear unit 6 is disposed in a casing 50. The planetary gear unit is driven by a sun gear unit connected to a motor. The planetary gear unit has a plurality of planetary gears 61 installed on a planetary arm 60 provided with an output shaft. In the planetary gear 61, inner teeth on an inner wall of the casing 50 mesh with the sun gear, the planetary gear is provided with a spur gear section 62 and a helical gear section 63. An inner spur gear 51 corresponding to the spur gear section 62 is formed on the casing 50, and a helical gear section 71 corresponding to the helical gear section 63 is formed on the sun gear 70. Number of repeated meshing of the planetary gear unit is reduced when the planetary gear 61 is rotated to reduce wear quantity and extend useful life. The back surface gap can be adjusted during when the reducer is assembled, a back surface gap automatic adjustment action is shown when the gear wears, and meshing is ensured, by using the corresponding helical gear sections 63, 71. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は遊星式歯車減速機構に関し、特に磨耗と損壊の問題を低減可能で、運転をさらにスムーズにすることができる低背面間隙精密遊星式歯車減速機構に関する。   The present invention relates to a planetary gear speed reduction mechanism, and more particularly, to a low back clearance precision planetary gear speed reduction mechanism that can reduce the problems of wear and damage and can further smooth operation.

動力源であるモーターは、受動部品を直接駆動する等、通常は回転速度が比較的速いため、回転速度が速過ぎ、慣性量が高くトルク低減の現象を招き、受動部品の構造を損壊させ、使用寿命に影響を及ぼす恐れがあり、同時に、操作の利便性と安全性にも影響を与えるため、一般に、モーターの出力軸上には減速機を設置し、回転速度を低下させる。減速機の種類は非常に多く、伝統的な大小の歯車を対応させる方式により、減速の目的を達成する構造の他に、現在最もよく目にする構造は、特許文献１、特許文献２、特許文献３等の遊星式歯車減速機構である。これら遊星式歯車減速機構は、体積が大きく、構造が複雑で、運転時に騒音と震動を生じる、という伝統的な減速機構が抱える問題を解決することができるため、様々に運用されている。   The motor that is the power source usually has a relatively high rotational speed, such as driving the passive component directly, so the rotational speed is too high, the inertia amount is high, causing the phenomenon of torque reduction, and the structure of the passive component is damaged. Generally, a reduction gear is installed on the output shaft of the motor to reduce the rotation speed because it may affect the service life and at the same time affect the convenience and safety of operation. There are many kinds of speed reducers, and besides the structure that achieves the purpose of speed reduction by using a system that corresponds to traditional large and small gears, the structures that are most commonly seen at present are Patent Document 1, Patent Document 2, Patent This is a planetary gear reduction mechanism as described in Reference 3. These planetary gear speed reduction mechanisms are used in various ways because they can solve the problems of traditional speed reduction mechanisms that are large in volume, complicated in structure, and generate noise and vibration during operation.

図１に示すように従来の遊星式歯車機構は、内歯刻みを備える殻体１０内に、遊星歯車ユニット２０を設置する。出力軸を備える該遊星歯車ユニット２０は、外縁に歯刻みを備える複数の遊星歯車２１により構成し、該各遊星歯車２１は、該殻体１０の内歯刻みと相互に噛み合い、噛み合い部Aを形成し、しかも該遊星歯車ユニット２０内には、モーターに連接する太陽歯車ユニット３０を設置する。該太陽歯車ユニット３０は、太陽歯車３１を備え、該太陽歯車３１と該各遊星歯車２１との間は、相対して噛み合い、それぞれ噛み合い部Bを形成する。これによりモーターが回転する時、該太陽歯車ユニット３０の太陽歯車３１を通して、該遊星歯車ユニット２０の遊星歯車２１を作動させ、該殻体１０に対して回転させ、このようにして遊星歯車ユニット２０出力軸の回転速度を低下させる目的を達成する。   As shown in FIG. 1, in the conventional planetary gear mechanism, a planetary gear unit 20 is installed in a shell 10 having an internal gear. The planetary gear unit 20 provided with an output shaft is constituted by a plurality of planetary gears 21 having teeth on the outer edge, and each planetary gear 21 meshes with the inner teeth of the shell 10 to form a meshing portion A. In addition, a sun gear unit 30 connected to the motor is installed in the planetary gear unit 20. The sun gear unit 30 includes a sun gear 31, and the sun gear 31 and the planetary gears 21 mesh with each other to form meshing portions B, respectively. Accordingly, when the motor rotates, the planetary gear 21 of the planetary gear unit 20 is operated through the sun gear 31 of the sun gear unit 30 and rotated with respect to the shell body 10, and thus the planetary gear unit 20. To achieve the purpose of reducing the rotation speed of the output shaft.

上記した構造は、減速の目的を達成することはできるが、該遊星歯車２１と該太陽歯車３１は、加工誤差等の素因により、組み立て時に、背面間隙が過大或いは過小であるという現象が生じる。よって、組み立て時に校正を繰り返し行い、背面間隙が比較的適した組合せを模索しなければならない。これでは時間の浪費で、また組み立ての難度とコストを拡大させ、さらには、遊星歯車２１と太陽歯車３１の最適な背面間隙組合せの達成が容易でないため、使用の性能と寿命に悪影響を及ぼす。   Although the above-described structure can achieve the purpose of speed reduction, the planetary gear 21 and the sun gear 31 have a phenomenon that the back gap is excessive or small at the time of assembly due to factors such as machining errors. Therefore, it is necessary to repeatedly perform calibration at the time of assembly and search for a combination in which the back gap is relatively suitable. This wastes time and increases the difficulty and cost of assembly, and further, since it is not easy to achieve the optimum back gap combination of the planetary gear 21 and the sun gear 31, it adversely affects the performance and life of use.

該遊星歯車ユニット２０の遊星歯車２１は、周縁の歯刻みが、該殻体１０及び該太陽歯車３１の歯刻みと相互に噛み合うことで回転するため、該遊星歯車２１と該殻体１０の内歯刻みが相互に噛み合い作動後、さらに該太陽歯車３１と噛み合い作動する必要がある。よって、それが受ける磨耗量は比較的多く、これにより遊星歯車２１は磨耗量が多くなり、該殻体１０及び該太陽歯車３１との間には、間隙が形成され易い。これでは、減速機構が容易に損壊してしまう他に、該殻体１０、該遊星歯車２１と該太陽歯車３１は、加工精度と磨耗により背面間隙が生じてしまう。背面間隙は調節できないため、回転時の震動と騒音を引き起こし、さらにひどい場合には、磨耗により遊星歯車噛み合いの誤差を招き、機器を破壊してしまい、遊星式歯車減速機構の使用寿命に重大な影響を及ぼす。   The planetary gear 21 of the planetary gear unit 20 is rotated by the peripheral teeth being meshed with the teeth of the shell 10 and the sun gear 31, so that the planetary gear 21 and the shell 10 It is necessary to further engage with the sun gear 31 after the tooth notches engage with each other. Therefore, the amount of wear that it receives is relatively large, and thus the planetary gear 21 has a large amount of wear, and a gap is easily formed between the shell 10 and the sun gear 31. As a result, the speed reduction mechanism is easily damaged, and the shell 10, the planetary gear 21 and the sun gear 31 have back gaps due to processing accuracy and wear. Since the back clearance cannot be adjusted, it causes vibration and noise during rotation. affect.

すなわち、従来の遊星式歯車減速機構は、磨耗面積が繰り返されるため、磨耗により震動、騒音、使用寿命の短縮という減少を招いており、改良が必要である。本発明は、従来の遊星式歯車減速機構の上記した欠点に鑑みてなされたもので、自動調節が可能で、磨耗量が大きく、背面間隙が生じた後にも調節ができないという従来の技術に存在する欠点を克服することができる。   In other words, the conventional planetary gear speed reduction mechanism has a repeated wear area, which causes a decrease in vibration, noise, and shortened service life due to wear, and needs to be improved. The present invention has been made in view of the above-mentioned drawbacks of the conventional planetary gear speed reduction mechanism, and is present in the prior art that can be automatically adjusted, has a large amount of wear, and cannot be adjusted even after a back gap has occurred. You can overcome the drawbacks.

中華民国特許公告第４６３８９２号Taiwan Patent Publication No. 463892 中華民国特許公告第５８２４６１号Taiwan Patent Publication No. 582461 米国特許第５,６８７,４８０号US Pat. No. 5,687,480

本発明が解決しようとする課題は、遊星歯車の磨耗量を減少させ、しかも背面間隙が生じた後には、噛み合いを微調節することができ、使用寿命を延長し、噛み合い精度を高めることができる低背面間隙精密遊星式歯車減速機構を提供することである。   The problem to be solved by the present invention is that the amount of wear of the planetary gear is reduced, and after the back gap is generated, the meshing can be finely adjusted, the service life can be extended, and the meshing accuracy can be increased. A low back clearance precision planetary gear reduction mechanism is provided.

上記課題を解決するため、本発明は下記の低背面間隙精密遊星式歯車減速機構を提供する。
低背面間隙精密遊星式歯車減速機構は、殻体、遊星歯車ユニット、太陽歯車ユニットを備え、
該殻体は環状体を呈し、該殻体の内縁には内平歯を備える。
該遊星歯車ユニットは、該殻体内に設置し、該遊星歯車ユニットは、出力軸を備える遊星アームにより構成し、該遊星アームは、該殻体内において複数の遊星歯車を設置し、該各遊星歯車の外縁には、該殻体内平歯と噛み合う平歯セクションを形成し、また該各遊星歯車は、平歯セクションの外縁とは異なり、中心へと向かう斜歯セクションを形成する。
該太陽歯車ユニットは、該遊星歯車ユニット間に設置し、該太陽歯車ユニットは、モーターと接続して駆動する太陽歯車を備え、該太陽歯車の外縁は斜歯セクションを呈し、該斜歯セクションは、該遊星歯車の斜歯セクションに対応する。 In order to solve the above-mentioned problems, the present invention provides the following low back clearance precision planetary gear reduction mechanism.
The low back clearance precision planetary gear reduction mechanism comprises a shell, planetary gear unit, sun gear unit,
The shell has an annular shape and has inner flat teeth on the inner edge of the shell.
The planetary gear unit is installed in the shell, and the planetary gear unit is configured by a planetary arm having an output shaft, and the planetary arm has a plurality of planetary gears installed in the shell, and each planetary gear On the outer edge, a spur tooth section that meshes with the flat tooth in the shell is formed, and each planetary gear forms an inclined tooth section toward the center, unlike the outer edge of the spur tooth section.
The sun gear unit is installed between the planetary gear units, and the sun gear unit includes a sun gear that is connected to and driven by a motor, and an outer edge of the sun gear has a bevel tooth section, and the bevel tooth section is , Corresponding to the inclined section of the planetary gear.

本発明は、遊星式歯車減速機構の磨耗を減少させることができ、しかもその使用寿命を延長でき、同時に背面間隙を生じても、調節が可能であるため、その噛み合いの確実性を高めることができる。さらに、震動と騒音を低下させる機能をも備えるため、その付加価値を高め、製品の競争力とコストパフォーマンスを強化することができる。   The present invention can reduce the wear of the planetary gear speed reduction mechanism, extend its service life, and at the same time can be adjusted even if a back clearance is generated, so that the reliability of the meshing can be improved. it can. Furthermore, since it also has a function to reduce vibration and noise, it can increase the added value and enhance the competitiveness and cost performance of the product.

歯車の噛み合い状態を説明する従来の遊星式歯車減速機構の断面概略図である。It is the cross-sectional schematic of the conventional planetary gear reduction mechanism explaining the meshing state of a gearwheel. 遊星歯車と太陽歯車及び殻体内のこぎり歯刻み間の位置関係を説明する従来の遊星式歯車減速機構の断面概略図である。It is the cross-sectional schematic diagram of the conventional planetary gear reduction mechanism explaining the positional relationship between a planetary gear, a sun gear, and a sawtooth step in a shell. 歯車の噛み合い状態を説明する本発明一実施形態による遊星式歯車減速機構の断面概略図である。1 is a schematic cross-sectional view of a planetary gear reduction mechanism according to an embodiment of the present invention, illustrating a meshing state of gears. 歯車の噛み合い状態を掲示する本発明一実施形態による遊星式歯車減速機構において、第二実施形態を示す断面概略図である。FIG. 5 is a schematic cross-sectional view showing a second embodiment of a planetary gear reduction mechanism according to an embodiment of the present invention that posts the meshing state of gears.

以下に図面を参照しながら本発明を実施するための最良の形態について詳細に説明する。本発明は、磨耗量が少なく、背面間隙を調節可能な遊星式歯車減速機構で、図示の具体的実施形態及びその構成部品において、前と後、左と右、頂点部と底部、上部と下部、水平と垂直に関しては、すべて説明の便のために用いるのみで、本発明を限定するものではなく、また本発明の構成部材を任意の位置、或いは空間に限定するものでもない。図と説明書中において指定するサイズは、本発明の特許請求範囲を離脱しない範囲において、本発明の実施形態の設計と必要に基づき、変化を加えることができる。   The best mode for carrying out the present invention will be described in detail below with reference to the drawings. The present invention is a planetary gear reduction mechanism with a small amount of wear and an adjustable back clearance, and in the illustrated specific embodiment and its components, front and rear, left and right, apex and bottom, top and bottom The horizontal and vertical directions are used only for convenience of explanation, and do not limit the present invention, and the constituent members of the present invention are not limited to arbitrary positions or spaces. The size specified in the drawings and the description can be changed based on the design and necessity of the embodiment of the present invention without departing from the scope of claims of the present invention.

図３示すように、本発明一実施形態による低背面間隙精密遊星式歯車減速機構は、中空の殻体５０、殻体５０内に設置し、出力軸を備える遊星歯車ユニット６、遊星歯車ユニット６内に設置し、しかもモーターに接続し駆動する太陽歯車ユニット７からなる。   As shown in FIG. 3, a low back clearance precision planetary gear speed reduction mechanism according to an embodiment of the present invention is a hollow shell 50, a planetary gear unit 6 installed in the shell 50 and having an output shaft, and the planetary gear unit 6 The sun gear unit 7 is installed inside and connected to a motor for driving.

殻体５０内縁には、遊星歯車ユニット６と噛み合う内平歯５１を備え、遊星歯車ユニット６は、遊星アーム６０を備える。しかも、遊星アーム６０は、殻体５０内に複数の遊星歯車６１を設置し、各遊星歯車６１の外縁には、平歯セクション６２を形成する。平歯セクション６２は、殻体５０の内平歯５１に対応し、また各遊星歯車６１は、平歯セクション６２の外縁とは異なり、中心へと向かう斜歯セクション６３を形成する。これにより太陽歯車ユニット７と噛み合い、しかも斜歯セクション６３の傾斜角度は約１.５度から３度で、本発明は２度を最適実施形態とする。   The inner edge of the shell 50 includes inner spur teeth 51 that mesh with the planetary gear unit 6, and the planetary gear unit 6 includes a planetary arm 60. Moreover, the planetary arm 60 has a plurality of planetary gears 61 installed in the shell 50, and a spur tooth section 62 is formed on the outer edge of each planetary gear 61. The spur tooth section 62 corresponds to the inner spur tooth 51 of the shell 50, and each planetary gear 61 forms an inclined tooth section 63 toward the center, unlike the outer edge of the spur tooth section 62. This meshes with the sun gear unit 7, and the inclination angle of the inclined tooth section 63 is about 1.5 to 3 degrees, and the present invention sets 2 degrees as the optimum embodiment.

太陽歯車ユニット７は、モーターを接続し駆動する太陽歯車７０を備え、太陽歯車７０の外縁は、斜歯セクション７１を呈する。斜歯セクション７１は、遊星歯車ユニット６の各遊星歯車６１の斜歯セクション６３に対応する。斜歯セクション７１の傾斜角度は、約１.５度から３度で、本発明は２度を最適実施形態とする。これにより、太陽歯車７０は同時に、遊星歯車ユニット６の各遊星歯車６１と噛み合い、しかも太陽歯車７０は前後位置を利用し、遊星歯車６１に対して、背面間隙の調節を行う。これにより、磨耗を減少させ、しかも背面間隙を調節可能な低背面間隙精密遊星式歯車減速機構を構成する。   The sun gear unit 7 includes a sun gear 70 that connects and drives a motor. The outer edge of the sun gear 70 presents a bevel tooth section 71. The inclined tooth section 71 corresponds to the inclined tooth section 63 of each planetary gear 61 of the planetary gear unit 6. The inclination angle of the inclined tooth section 71 is about 1.5 to 3 degrees, and 2 degrees is the preferred embodiment of the present invention. As a result, the sun gear 70 meshes with the planetary gears 61 of the planetary gear unit 6 at the same time, and the sun gear 70 adjusts the back clearance with respect to the planetary gear 61 using the front and rear positions. This constitutes a low back clearance precision planetary gear reduction mechanism that reduces wear and that can adjust the back clearance.

上記した構造設計を通して、本発明は実際の運用時に、図３に示すように、太陽歯車ユニット７の太陽歯車７０がモーター（図示なし）の駆動受け、回転する時、太陽歯車７０を通して、遊星アーム６０上の遊星歯車６１を作動させる。並びに、遊星歯車６１の、殻体５０内縁の内平歯５１に相対する回転の関係により、遊星アーム６０の出力端は、減速出力を実現し、遊星歯車ユニット６の遊星歯車６１は、平歯セクション６２と斜歯セクション６３を利用し、それぞれ殻体５０の内平歯５１及び太陽歯車７０の斜歯セクション７１と噛み合う。   Through the above-described structural design, the present invention, in actual operation, as shown in FIG. 3, when the sun gear 70 of the sun gear unit 7 is driven by a motor (not shown) and rotates, the planetary arm passes through the sun gear 70 when rotating. The planetary gear 61 on 60 is activated. In addition, due to the rotational relationship of the planetary gear 61 relative to the inner flat tooth 51 of the inner edge of the shell 50, the output end of the planetary arm 60 achieves a reduction output, and the planetary gear 61 of the planetary gear unit 6 has a flat tooth. The section 62 and the inclined tooth section 63 are used to mesh with the inner flat tooth 51 of the shell 50 and the inclined tooth section 71 of the sun gear 70, respectively.

よって、本発明一実施形態の遊星歯車６１と太陽歯車７０は、たとえ加工誤差が存在していたとしても、対応する斜歯セクション６３、７１を設置するため、組み立て時に自動的に校正され、背面間隙が過大或いは過小となる、従来の構造に存在する問題は発生しない。つまり、組合せ及び組み立てが容易であるという効果を備え、組み立ての利便性を増進し、しかも製造と組み立てのコストを低下させることができ、使用における性能を向上させ、使用寿命を延長することができる。   Therefore, the planetary gear 61 and the sun gear 70 according to the embodiment of the present invention are automatically calibrated at the time of assembly to install the corresponding inclined tooth sections 63 and 71 even if processing errors exist, There is no problem with conventional structures where the gap is too large or too small. In other words, it has the effect of being easy to combine and assemble, enhances the convenience of assembly, reduces the cost of manufacturing and assembly, improves the performance in use, and extends the service life. .

また、遊星歯車６１は、平歯セクション６２及び斜歯セクション６３と殻体５０及び太陽歯車７０によりそれぞれ噛み合うため、同時に噛み合い磨耗するという従来の構造に存在する問題は発生しない。本発明遊星歯車６１の同一歯面の磨耗量は、大幅に減り、遊星歯車６１の平歯セクション６２は、殻体５０の内歯刻みとだけ噛み合い、遊星歯車６１の斜歯セクション６３は、太陽歯車７０とだけ噛み合い作動する。このようにして、遊星歯車６１と殻体５０内歯刻み及び太陽歯車７０の噛み合い位置区間をずらすことができ、これにより遊星歯車６１の磨耗を減らし、ひいては遊星歯車６１の使用寿命を延長することができる。   Further, since the planetary gear 61 is engaged with the spur tooth section 62 and the inclined tooth section 63 by the shell 50 and the sun gear 70, respectively, there is no problem that exists in the conventional structure that meshes and wears at the same time. The amount of wear on the same tooth surface of the planetary gear 61 of the present invention is greatly reduced, the spur tooth section 62 of the planetary gear 61 meshes only with the internal teeth of the shell 50, and the bevel tooth section 63 of the planetary gear 61 Only the gear 70 engages. In this way, the meshing position of the planetary gear 61 and the shell 50 and the meshing position of the sun gear 70 can be shifted, thereby reducing the wear of the planetary gear 61 and thus extending the service life of the planetary gear 61. Can do.

さらに、遊星歯車６１に、磨耗或いは加工誤差により背面間隙が生じる時には、遊星歯車６１と太陽歯車７０の斜歯セクション６３、７１の係合関係を利用し、噛み合い調整の作用を生じることができる。これにより、その噛み合いの確実性を確保し、遊星歯車６１と太陽歯車７０の運転をさらに一層スムーズとし、震動と騒音の発生を減らすことができ、さらに不要な磨耗を回避し、噛み合いの誤差の発生を防止し、さらにその使用寿命を延長することができる。   Further, when a back clearance is generated in the planetary gear 61 due to wear or processing errors, the engagement relationship between the planetary gear 61 and the inclined tooth sections 63 and 71 of the sun gear 70 can be utilized to produce a meshing adjustment effect. As a result, the reliability of the meshing can be ensured, the planetary gear 61 and the sun gear 70 can be operated more smoothly, the occurrence of vibration and noise can be reduced, unnecessary wear can be avoided, and meshing errors can be reduced. Occurrence can be prevented and the service life can be extended.

図４は、歯車の噛み合い状態を掲示する本発明一実施形態による遊星式歯車減速機構において、第二実施形態を示す断面概略図である。図４に示すように、殻体５０内縁には、遊星歯車ユニット６が噛み合う内斜歯５２を備え、遊星歯車６は遊星アーム６０を備え、しかも、遊星アーム６０は、殻体５０内に複数の遊星歯車６５を設置する。各遊星歯車６５の外縁には、斜歯セクション６６を形成し、斜歯セクション６６は、殻体５０の内斜歯５２に対応し、しかも内斜歯５２と斜歯セクション６６の傾斜角度は約１.５度から３度で、本発明は２度を最適実施形態とする。これにより、遊星歯車６５は、前後位置を利用し、殻体５０に対して背面間隙を自動的に調節する。   FIG. 4 is a schematic cross-sectional view showing a second embodiment of a planetary gear speed reduction mechanism according to an embodiment of the present invention that posts the meshing state of gears. As shown in FIG. 4, the inner edge of the shell 50 is provided with inner inclined teeth 52 with which the planetary gear unit 6 is engaged. The planetary gear 6 is provided with a planetary arm 60, and a plurality of planetary arms 60 are provided in the shell 50. The planetary gear 65 is installed. An inclined tooth section 66 is formed on the outer edge of each planetary gear 65, and the inclined tooth section 66 corresponds to the inner inclined tooth 52 of the shell 50, and the inclination angle between the inner inclined tooth 52 and the inclined tooth section 66 is approximately. From 1.5 degrees to 3 degrees, the present invention sets 2 degrees as the optimum embodiment. As a result, the planetary gear 65 automatically adjusts the rear gap with respect to the shell 50 using the front-rear position.

各遊星歯車６５は、斜歯セクション６５の外縁とは異なり、平歯セクション６７を形成し、これにより太陽歯車ユニット７と噛み合う。太陽歯車ユニット７は、モーターに接続し駆動する太陽歯車７０を備え、太陽歯車７０の外縁は平歯セクション７２を呈する。平歯セクション７２は、遊星歯車ユニット６の各遊星歯車６５の平歯セクション６７に対応し、これにより太陽歯車７０は、遊星歯車ユニット６の各遊星歯車６５と同時に噛み合い、上記した第一実施形態と相同の機能と効果を備える。   Each planetary gear 65 forms a spur tooth section 67, which is different from the outer edge of the bevel tooth section 65, thereby meshing with the sun gear unit 7. The sun gear unit 7 includes a sun gear 70 that is connected to and driven by a motor, and the outer edge of the sun gear 70 presents a spur section 72. The spur tooth section 72 corresponds to the spur tooth section 67 of each planetary gear 65 of the planetary gear unit 6, whereby the sun gear 70 meshes simultaneously with each planetary gear 65 of the planetary gear unit 6, and the first embodiment described above. And has similar functions and effects.

本発明の技術特徴に基づき、太陽歯車７０と遊星歯車６５斜歯セクション６６の噛み合いの特徴は、遊星歯車６５と殻体５０の相互歯車の噛み合いにおいて使用し、その平歯セクション噛み合いの特徴を、斜歯方式の噛み合いの特徴に変えるだけで、相同の機能を発揮することができる。   In accordance with the technical features of the present invention, the meshing feature of the sun gear 70 and the planetary gear 65 inclined tooth section 66 is used in the meshing of the planetary gear 65 and the shell 50 with each other, and the spur tooth section meshing feature is used. A homologous function can be exhibited simply by changing to the meshing characteristics of the inclined tooth system.

１０ 殻体
２０ 遊星歯車ユニット
２１ 遊星歯車
３０ 太陽歯車ユニット
３１ 太陽歯車
A 噛み合い部
B 噛み合い部
５０ 殻体
５１ 内平歯
５２ 内斜歯
６ 遊星歯車ユニット
６０ 遊星アーム
６１ 遊星歯車
６２ 平歯セクション
６３ 斜歯セクション
６５ 遊星歯車
６６ 斜歯セクション
６７ 平歯セクション
７ 太陽歯車ユニット
７０ 太陽歯車
７１ 斜歯セクション
７２ 平歯セクション DESCRIPTION OF SYMBOLS 10 Shell 20 Planetary gear unit 21 Planetary gear 30 Sun gear unit 31 Sun gear
A meshing part
B meshing part 50 shell 51 inner flat tooth 52 inner inclined tooth 6 planetary gear unit 60 planetary arm 61 planetary gear 62 flat tooth section 63 inclined tooth section 65 planetary gear 66 inclined tooth section 67 flat tooth section 7 sun gear unit 70 sun gear 71 Inclined tooth section 72 Flat tooth section

Claims (7)

低背面間隙精密遊星式歯車減速機構は、殻体、遊星歯車ユニット、太陽歯車ユニットを備え、
前記殻体は環状体を呈し、前記殻体の内縁には内平歯を備え、
前記遊星歯車ユニットは、前記殻体内に設置し、前記遊星歯車ユニットは、出力軸を備える遊星アームにより構成し、前記遊星アームは、前記殻体内において複数の遊星歯車を設置し、前記各遊星歯車の外縁には、前記殻体内平歯と噛み合う平歯セクションを形成し、また前記各遊星歯車は、平歯セクションの外縁とは異なり、中心へと向かう斜歯セクションを形成し、
前記太陽歯車ユニットは、前記遊星歯車ユニット間に設置し、前記太陽歯車ユニットは、モーターと接続して駆動する太陽歯車を備え、前記太陽歯車の外縁は斜歯セクションを呈し、前記斜歯セクションは、前記遊星歯車の斜歯セクションに対応することを特徴とする低背面間隙精密遊星式歯車減速機構。 The low back clearance precision planetary gear reduction mechanism comprises a shell, planetary gear unit, sun gear unit,
The shell body has an annular body, and the inner edge of the shell body has inner flat teeth,
The planetary gear unit is installed in the shell, and the planetary gear unit is constituted by a planetary arm having an output shaft, and the planetary arm has a plurality of planetary gears installed in the shell, and each planetary gear A flat tooth section that meshes with the shell flat teeth is formed on the outer edge of the shell, and each planetary gear forms an inclined tooth section toward the center, unlike the outer edge of the flat tooth section,
The sun gear unit is installed between the planetary gear units, and the sun gear unit includes a sun gear that is connected to and driven by a motor, and an outer edge of the sun gear exhibits a bevel tooth section, and the bevel tooth section is A low back clearance precision planetary gear reduction mechanism that corresponds to the bevel tooth section of the planetary gear. 前記遊星歯車と前記太陽歯車の斜歯セクションの傾斜角度は約１.５度から３度で、これにより前記太陽歯車は、前後位置を利用し、前記遊星歯車に相対して背面間隙を自動的に調節することを特徴とする請求項１に記載の低背面間隙精密遊星式歯車減速機構。   The inclination angle of the inclined section of the planetary gear and the sun gear is about 1.5 to 3 degrees, so that the sun gear automatically uses the front-rear position and automatically sets the back clearance relative to the planetary gear. The low back clearance precision planetary gear reduction mechanism according to claim 1, wherein 前記遊星歯車と前記太陽歯車の斜歯セクションの傾斜角度は、約２度で、これにより前記太陽歯車は、前後位置を利用し、前記遊星歯車に相対して背面間隙を自動的に調節することを特徴とする請求項１或いは２に記載の低背面間隙精密遊星式歯車減速機構。   The inclination angle of the bevel tooth section of the planetary gear and the sun gear is about 2 degrees, so that the sun gear automatically adjusts the back clearance relative to the planetary gear using the front-rear position. The low back clearance precision planetary gear reduction mechanism according to claim 1 or 2. 低背面間隙精密遊星式歯車減速機構は、殻体、遊星歯車ユニット、太陽歯車ユニットを備え、
前記殻体は環状体を呈し、前記殻体の内縁には内斜歯を備え、
前記遊星歯車ユニットは、前記殻体内に設置し、前記遊星歯車ユニットは、出力軸を備える遊星アームにより構成し、前記遊星アームは、前記殻体内において複数の遊星歯車を設置し、前記各遊星歯車の外縁には、前記殻体内斜歯と噛み合う斜歯セクションを形成し、また前記各遊星歯車は、斜歯セクションの外縁とは異なり、平歯セクションを形成し、
前記太陽歯車ユニットは、前記遊星歯車ユニット間に設置し、前記太陽歯車ユニットは、モーターと接続して駆動する太陽歯車を備え、前記太陽歯車の外縁は平歯セクションを呈し、前記平歯セクションは、前記遊星歯車の平歯セクションに対応することを特徴とする低背面間隙精密遊星式歯車減速機構。 The low back clearance precision planetary gear reduction mechanism comprises a shell, planetary gear unit, sun gear unit,
The shell body has an annular body, and the inner edge of the shell body has inner inclined teeth;
The planetary gear unit is installed in the shell, and the planetary gear unit is constituted by a planetary arm having an output shaft, and the planetary arm has a plurality of planetary gears installed in the shell, and each planetary gear The outer edge of each of the planetary gears forms an oblique tooth section that meshes with the internal oblique tooth of the shell, and each planetary gear forms a flat tooth section, unlike the outer edge of the oblique tooth section,
The sun gear unit is installed between the planetary gear units, and the sun gear unit includes a sun gear connected to and driven by a motor, and an outer edge of the sun gear exhibits a spur tooth section, and the spur tooth section is A low back clearance precision planetary gear reduction mechanism corresponding to a spur tooth section of the planetary gear. 前記殻体の内斜歯と前記遊星歯車の斜歯セクションの傾斜角度は約１.５度から３度で、これにより前記遊星歯車は、前後位置を利用し、前記殻体に相対して背面間隙を自動的に調節することを特徴とする請求項４に記載の低背面間隙精密遊星式歯車減速機構。   The inclination angle of the inner inclined tooth of the shell and the inclined tooth section of the planetary gear is about 1.5 degrees to 3 degrees, so that the planetary gear uses the front-rear position and is opposed to the shell. 5. The low back clearance precision planetary gear reduction mechanism according to claim 4, wherein the clearance is automatically adjusted. 前記殻体の内斜歯と前記遊星歯車の斜歯セクションの傾斜角度は約２度で、これにより前記遊星歯車は、前後位置を利用し、前記殻体に相対して背面間隙を自動的に調節することを特徴とする請求項４或いは５に記載の低背面間隙精密遊星式歯車減速機構。   The inclination angle of the inner inclined tooth of the shell and the inclined tooth section of the planetary gear is about 2 degrees, so that the planetary gear automatically uses the front-rear position and automatically sets the back gap relative to the shell. 6. The low back clearance precision planetary gear reduction mechanism according to claim 4 or 5, wherein adjustment is performed. 低背面間隙精密遊星式歯車減速機構は、殻体、遊星歯車ユニット、太陽歯車ユニットを備え、
前記殻体は環状体を呈し、前記殻体の内縁には内斜歯を備え、
前記遊星歯車ユニットは、前記殻体内に設置し、前記遊星歯車ユニットは、出力軸を備える遊星アームにより構成し、前記遊星アームは、前記殻体内において複数の遊星歯車を設置し、前記各遊星歯車の外縁には、前記殻体内斜歯と噛み合う斜歯セクションを形成し、また前記各遊星歯車は、斜歯セクションの外縁とは異なり、中心へと向かう別の斜歯セクションを形成し、
前記太陽歯車ユニットは、前記遊星歯車ユニット間に設置し、前記太陽歯車ユニットは、モーターと接続して駆動する太陽歯車を備え、前記太陽歯車の外縁は斜歯セクションを呈し、前記斜歯セクションは、前記遊星歯車の中心へと向かう斜歯セクションに対応することを特徴とする低背面間隙精密遊星式歯車減速機構。 The low back clearance precision planetary gear reduction mechanism comprises a shell, planetary gear unit, sun gear unit,
The shell body has an annular body, and the inner edge of the shell body has inner inclined teeth;
The planetary gear unit is installed in the shell, and the planetary gear unit is constituted by a planetary arm having an output shaft, and the planetary arm has a plurality of planetary gears installed in the shell, and each planetary gear The outer edge of each of the planetary gears forms an oblique tooth section that meshes with the inner oblique tooth of the shell, and each planetary gear forms a different oblique tooth section toward the center, unlike the outer edge of the oblique tooth section,
The sun gear unit is installed between the planetary gear units, and the sun gear unit includes a sun gear that is connected to and driven by a motor, and an outer edge of the sun gear exhibits a bevel tooth section, and the bevel tooth section is A low back clearance precision planetary gear reduction mechanism corresponding to an inclined tooth section toward the center of the planetary gear.
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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014031886A (en) * 2012-07-31 2014-02-20 Premium Stefan Hameln Zweigniederlassung Der Premium Stefan Bv Planetary gear apparatus and operation apparatus configured by including planetary gear
CN111245157A (en) * 2020-03-25 2020-06-05 点前传动机械(上海)有限公司 180-degree limiting reciprocating motion precision planetary gear speed reduction motor

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JPH05180276A (en) * 1991-05-23 1993-07-20 Takashi Takahashi Planetary gear speed changer
JPH06257646A (en) * 1993-03-02 1994-09-16 Shimpo Ind Co Ltd Mechanical reduction gear
JP2001525044A (en) * 1997-05-15 2001-12-04 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト Planetary gear set
JP2002174304A (en) * 2000-12-04 2002-06-21 Minebea Co Ltd Epicycle reduction gear with torque limiter function

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05180276A (en) * 1991-05-23 1993-07-20 Takashi Takahashi Planetary gear speed changer
JPH06257646A (en) * 1993-03-02 1994-09-16 Shimpo Ind Co Ltd Mechanical reduction gear
JP2001525044A (en) * 1997-05-15 2001-12-04 ツェットエフ、フリードリッヒスハーフェン、アクチエンゲゼルシャフト Planetary gear set
JP2002174304A (en) * 2000-12-04 2002-06-21 Minebea Co Ltd Epicycle reduction gear with torque limiter function

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2014031886A (en) * 2012-07-31 2014-02-20 Premium Stefan Hameln Zweigniederlassung Der Premium Stefan Bv Planetary gear apparatus and operation apparatus configured by including planetary gear
CN111245157A (en) * 2020-03-25 2020-06-05 点前传动机械(上海)有限公司 180-degree limiting reciprocating motion precision planetary gear speed reduction motor

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