JP2005114163A - Magnetic planetary gear device - Google Patents

Magnetic planetary gear device Download PDF

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JP2005114163A
JP2005114163A JP2004269888A JP2004269888A JP2005114163A JP 2005114163 A JP2005114163 A JP 2005114163A JP 2004269888 A JP2004269888 A JP 2004269888A JP 2004269888 A JP2004269888 A JP 2004269888A JP 2005114163 A JP2005114163 A JP 2005114163A
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magnetic
planetary gear
gear
teeth
meshing
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JP3942102B2 (en )
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Daichi Goto
Kingo Sotani
Katsuo Tsurumoto
大地 後藤
欽吾 操谷
勝夫 鶴本
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Shoei Koki:Kk
株式会社松栄工機
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PROBLEM TO BE SOLVED: To provide a magnetic planetary gear device having improved transmission property, solving problems on the vibration, noises and oiling of a conventional planetary gear utilizing mechanical meshing operation.
SOLUTION: The magnetic teeth of a magnetic sun gear is shaped so that they magnetically mesh with a magnetic planetary gear on the basis of quasi-inscribed meshing operation instead of circumscribed meshing operation which causes the pulsation of transmission torque, thus reducing the pulsation of transmission torque. Furthermore, the magnetic teeth of a magnetic external gear are partially removed for transmission torque balance in meshing between the magnetic planetary gear and the magnetic external gear and in meshing between the magnetic sun gear and the magnetic planetary gear, which improves transmission efficiency and reduced materials for the magnetic teeth, resulting in reduced material cost. The magnetic sun gear is in a paired structure with the magnetic planetary gear held therein, which increases power transmission torque.
COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、磁気伝達による無騒音、無塵、無給油を特徴とし、駆動側、被駆動側の各歯車に配設した永久磁石の磁気吸引または反発にてトルク伝達する磁気式遊星歯車装置に関するものである。 The present invention, no noise due to the magnetic transfer, dust-free, characterized by oil-free, drive-side, a magnetic type planetary gear device that the torque transmission by the magnetic attraction or repulsion of the permanent magnets arranged on the respective gears of the driven-side it is intended.

従来から知られている歯車の伝達システムの技術としては、(1)機械的な接触を伴う歯車による伝達方式を用いた構造、(2)学術段階ではあるが磁気力を利用して動力伝達を行う磁気式遊星歯車方式の構造などがあった。 Techniques transmission system of gears known in the prior art, the structure using a transmission system by gears with (1) a mechanical contact, a power transmission using a (2) is in the academic stage but the magnetic force It had such structure of the magnetic planetary gear system to perform.

特公平6−52096号公報 Kokoku 6-52096 Patent Publication No.

しかし(1)の機械的な接触を伴う噛み合いの伝達方式では、大きな動力伝達は可能であるが、振動、騒音、磨耗、摩擦による塵埃発生、それに伴う耐久性性能の劣化、又、定期的な給油が不可欠であるなどの構造的な課題を抱えている。 However, transmission method of the meshing involves mechanical contact (1) is susceptible large power transmission, vibration, noise, wear, dust generation, deterioration of the durability performance accompanying therewith by friction, also a regular refueling is having the structural issues, such as it is essential. 一方、(2)にて提案されている磁気式遊星歯車では、上記(1)に示す欠点は解消できるものの、動力伝達が比較的小さいことや、伝達トルクに脈動が大きいなどの欠点をもっており、利用範囲が極めて限定されている。 On the other hand, in the magnetic planetary gear proposed in (2), although disadvantages shown in the above (1) can be eliminated, it and the power transmission is relatively small, has a disadvantage of such pulsation is large transmitted torque, use range is very limited.

上記課題の解決のため本発明では、従来技術(1)に対しては、動力の伝達に磁気を用い、磁気の吸引力、及び反発力を利用して非接触で伝達することで解決せんとするものであり、従来の技術(2)に示した磁気式遊星歯車の構造に対しては、太陽歯車の磁気歯形状を、該太陽磁気歯と噛み合う遊星歯車の磁気歯が準内接かみ合いになるよう形成することで、伝達トルクの脈動を軽減したことを特徴としている。 In the present invention for solving the above problems, with respect to the prior art (1), using a magnetically power transmission, solved cent by transmitting utilizing the suction force, and the repulsive force of the magnetic contactlessly is intended to, with respect to the structure of the magnetic planetary gears shown in the prior art (2), the magnetic tooth shape of the sun gear, the magnetic teeth of the planetary gears meshing with said sun magnetic teeth meshing quasi inscribed by so as form, it is characterized in that to reduce the pulsation of the transmitted torque.

さらに、本発明に使用する永久磁石を効果的に使用するため、磁気歯の磁気歯たけ(本実施例では動力伝達への寄与が比較的少ない磁気式外輪歯車の外周部を削減した)を短くして材料コストの削減を図ったものである。 Furthermore, in order to effectively use the permanent magnet used in the present invention, the magnetic tooth depth of the magnetic teeth (with reduced outer peripheral portion of relatively small magnetic ring gear contribution to power transmission in the present embodiment) shorter in which it attempted to reduce material costs by.

一方、伝達トルクを強くする方法として、一対の太陽歯車を使用して、遊星歯車の遊星盤を所望の空隙を有しつつ挟めた構造にすることにより、該遊星歯車装置の伝達トルクを約1.8倍に高めたことを特徴とするものである。 On the other hand, as a method for strongly transmitting torque, using a pair of sun gears, by a structure in which Hasame while the planetary plate of the planetary gear has a desired void, a transmission torque of the planetary gear about 1 is characterized in that the enhanced .8 times.

本発明の磁気式遊星歯車装置は、従来の機械式で構造的な課題となっていた、歯の機械的噛み合いによる騒音、塵埃の発生、又、定期的な給油、耐久性の劣化などの欠点を、伝達方式に永久磁石用いて磁気の吸引及び、反発を用いた磁気式の噛み合いにより非接触による動力伝達を実現することで改善し、又、メンテナンスフリー化も可能にするものである。 Magnetic planetary gear device of the present invention has been a structural problem in the conventional mechanical noise due to the engagement mechanical teeth, generation of dust, also disadvantages such periodic lubrication, durability deterioration the suction and magnetic using permanent magnets to the transmission system, and improved by realizing the power transmission by the non-contact by the engagement of the magnetic type using a repulsion, and is intended to allow also maintenance-free. 又、性能面では磁気的な噛み合いを準内接噛み合いにすることで、伝達トルクの脈動を軽減して伝達特性を大幅に改善するとともに、脈動がもたらす振動、騒音などを更に低減し、磁気式遊星歯車の品質、及び性能改善に大きな効果をもたらすものである。 Also, in terms of performance by the meshing semi inscribed magnetic engagement, as well as greatly improved relief to transfer characteristics of the pulsation of transmitted torque, vibration pulsation result, further reduce such noise, magnetic it is intended to provide a great effect on the quality of the planetary gears, and performance improvements.

一方、経済面では、伝達トルクの割り振りを適切に設定することで、使用する磁気歯の面積を少なくして永久磁石の材料費の軽減を図った磁気式遊星歯車装置を提供するものである。 On the other hand, in the economy, by appropriately setting the allocation of transmission torque, there is provided a magnetic planetary gear device which aimed to reduce the material cost of the permanent magnet by reducing the area of ​​the magnetic teeth to be used.

さらに、磁気式遊星歯車の課題でもある伝達しうる上限の伝達トルクを、太陽歯車を2個用いて形成することで、通常の伝達トルクの上限を約2倍に引き上げ、磁気式遊星歯車装置の応用範囲の拡大を図ったものである。 Further, the transmission torque of the upper limit that can be transmitted, which is also the problem of magnetic planetary gear is formed using two sun gears, raising the upper limit of the normal transmission torque about twice, the magnetic planetary gear unit is obtained expand its range of applications.

以下本発明の形態を図面に基づいて詳細に説明する。 The following forms of the present invention with reference to the drawings will be described in detail. 図1は従来より提案されている磁気式遊星歯車による1実施例であって、図1(イ)は該歯車の磁気的伝達システム部の構成を説明するためのスケルトン図、図1(ロ)は、図(イ)のA−A線に沿った磁気式遊星歯車装置の主要部の一部断面図である。 Figure 1 is a first embodiment according to the magnetic planetary gear have been proposed, FIG. 1 (b) is a skeleton diagram for explaining the configuration of a magnetic transfer system of the gear, FIG. 1 (b) is a partial cross-sectional view of a main part of a magnetic planetary gear device taken along line a-a of FIG. (b). 又、図中のN、及びSは永久磁石の磁気歯の極性を示したものである。 Further, N in the figure, and S shows the polarity of the magnetic teeth of the permanent magnet. 図1において、外輪歯車1は、磁性体からなる外輪盤11と、該外輪盤の外周部に放射状に、かつ、隣り合う磁気歯間に所定の隙間を設けて接着剤等で等間隔に配設された磁気歯12・・・で構成されている。 In Figure 1, the ring gear 1, distribution outer ring plate 11 made of a magnetic material, the radially outer periphery of the outer race plate, and, at regular intervals by an adhesive or the like with a predetermined gap between the adjacent magnetic teeth It is composed of a set by magnetic teeth 12,. 尚、該外輪歯車1は適宜手段にて磁気式遊星歯車装置のフレーム(図示せず)に固定されている。 Incidentally, the outer ring gear 1 is fixed to the frame of the magnetic planetary gear unit at a suitable means (not shown). 次に太陽歯車2は同様に磁性体からなる太陽盤21と、該太陽盤21の外周部に放射状に、かつ、隣り合う磁気歯間に所定の隙間を設けて接着剤等で等間隔に配設された磁気歯22及び、太陽盤21の中心部に該太陽盤面に垂直に圧入した太陽軸23から構成されている。 Then the solar panel 21 sun gear 2 is made of a likewise magnetic, radially outer peripheral portion of the solar panel 21, and distribution at equal intervals on the adhesive with a predetermined gap between the magnetic teeth adjacent like set the magnetic teeth 22 and, and a sun shaft 23 press-fitted perpendicularly to the solar board in the center of the solar panel 21. また該太陽歯車2は外輪歯車1に圧入した軸受け24を介してセットカラー25で回転自在に装着されている。 Also the sun gear 2 is rotatably mounted on the set collar 25 via a bearing 24 which is press-fitted into the ring gear 1. ここに磁気歯22・・・、磁気歯12・・・は同一平面に設定されている。 Here the magnetic teeth 22, ..., the magnetic teeth 12, ... are set on the same plane. 一方、遊星歯車3は、磁性体からなる遊星盤31と、その外周部に放射状にかつ、隣り合う磁気歯間に所定の隙間を設けて接着剤等で等間隔に配設された磁気歯32・・・で構成されており、遊星歯車盤35に軸受け34を介して回転自在にセットカラー33で装着されている。 On the other hand, the planetary gear 3, the planetary plate 31 made of a magnetic material, the magnetic teeth 32 the outer periphery thereof and radially, arranged at equal intervals with an adhesive or the like with a predetermined gap between the adjacent magnetic teeth ... is composed of, is mounted in rotatably Collars 33 through a bearing 34 in the planetary gear plate 35. 本従来例では該遊星歯車3は等間隔(120°)に3個(図1(ロ)では、2個は図示せず。)取り付けられており、該3個の遊星歯車3・・の磁気歯32・・・の表面は、同一平面に設定され、前記外輪歯12・・・と太陽歯22・・・の磁気歯平面と、所定の空隙を有し対向して磁気式遊星歯車の取り付け板(図示せず)に適宜手段にて回転自在に固着されている。 (In FIG. 1 (b), two not shown.) Three planetary gear 3 at equal intervals (120 °) in this conventional example is attached, the three planetary gears 3 ... Magnetic the surface of the tooth 32, ... are set on the same plane, the mounting of the magnetic planetary gear facing has a magnetic tooth plane of the outer ring teeth 12, ... and the sun teeth 22 ..., a predetermined gap It is rotatably secured by suitable means to the plate (not shown).

この従来例の磁気式遊星歯車装置の動力伝達について説明する。 For power transmission of the conventional magnetic type planetary gear device is described. 図1において、太陽歯車2を駆動側、遊星歯車3を被駆動側とした場合、太陽歯車2と遊星歯車3は、太陽歯車2の磁気歯22・・・と、遊星歯車3の磁気歯32・・・とが各々交互に配設したN極とS極の磁気的な噛み合いにより伝達される。 In Figure 1, the sun gear 2 driving side, when the planetary gear 3 and the driven side, the sun gear 2 and the planet gear 3, and the magnetic teeth 22, ... of the sun gear 2, the magnetic teeth 32 of the planetary gear 3 ... and it is transmitted by the N and S poles magnetic engagement of disposed respectively alternately. この場合の磁気的な噛み合いで、動力伝達に有効な噛み合い部(対向する磁気歯の極性がN極とS極となる状態を有効噛み合いという)は、斜線を施した数個のラグビーボールの形状をした部分(1b・・)となる。 In magnetic engagement in this case, effective meshing portions in the power transmission (polarity opposite to the magnetic teeth that mesh enabled state in which the N pole and the S pole), the shape of several rugby ball hatched becomes a portion (1b ··). 又、遊星歯車3の磁気歯32・・・と、取り付け板(図示せず)に固定された外輪歯車1の磁気歯12・・・は、同様に斜線を施した有効噛み合い部分(1a・・)で磁気的に噛み合って動力を伝達する。 Further, the magnetic teeth 32, ... of the planetary gear 3, the mounting plate magnetic teeth 12, ... of the outer gear 1 fixed to (not shown) is similarly effective hatched meshing portion (1a · · ) meshes magnetically by transmitting power. 尚、磁気式遊星歯車装置としての回転比、即ち太陽歯車2の回転数に対する遊星歯車軸36の回転数は、駆動側である太陽歯車2の歯数(16個)と、外輪歯車1の歯数(64)で決定され、歯数比4に遊星自転分1を加えた1/5回転の減速となる。 The rotation ratio of the magnetic planetary gear unit, that is, the rotation speed of the planetary gear shaft 36 with respect to the rotational speed of the sun gear 2, the number of teeth of the sun gear 2 is driven side (16), the teeth of the ring gear 1 It is determined by the number (64), the deceleration of the 1/5 rotation plus planetary rotation amount 1 to gear ratio 4.

次に、従来例の動力伝達トルクについて説明する。 Next, a description will be given power transmission torque of a conventional example. 磁気式遊星歯車装置としての伝達トルクは、遊星歯車と外輪歯車間の伝達トルク(主たるトルクは前述の磁気的な主噛み合い部1a・・の面積の3個分に概ね比例する)と、遊星歯車と太陽歯車間の伝達トルク(主たるトルクは前述の主噛み合い部1bの3個分に概ね比例する)の両者が関連して伝達されるため、両者の伝達トルクの小さい方が磁気式遊星歯車装置としての伝達トルクの限界トルクとなる。 The transmission torque of the magnetic planetary gear device, the transmission torque between the planetary gear and the ring gear (primary torque is approximately proportional to the 3 pieces of the area of ​​the aforementioned magnetic main engaging portion 1a · ·), the planetary gears a transmission torque between the sun gear (primary torque is approximately proportional to the three in the main engaging portion 1b of the above) because both are transmitted in connection with, smaller both the transmission torque of the magnetic planetary gear unit the limit torque of the torque transmitted as. 従来例の伝達トルクを測定した結果、後者(遊星歯車と太陽歯車の伝達トルク)が前者(遊星歯車と外輪歯車間の伝達トルク)に比べ概ね60%であった。 A result of measuring the transmission torque of the conventional example, the latter (the transmission torque of the planetary gear and the sun gear) was approximately 60% than the former (the transmission torque between the planetary gear and ring gear). これは、主たる伝達トルクが前述した有効噛み合い部(1a)、(1b)の噛み合い面積で比例することによる。 This is effective engagement portion to which the main transmission torque mentioned above (1a), due to proportionally meshing area (1b). この結果、磁気式遊星歯車装置の伝達トルクは後者の伝達トルクで規定され、前者の有する伝達トルクの40%が余裕となる。 As a result, the transmission torque of the magnetic planetary gear is defined by the latter transmitted torque, 40% of the transmitted torque with the former becomes margin.

図2、及び図3は本発明に係る磁気歯車装置の第一の実施例であって、図2(イ)はその遊星歯車装置の概略平面図、同(ロ)はその左側面図、(ハ)は右側面図である。 2, and 3 is a first embodiment of a magnetic gearing according to the present invention, FIG. 2 (b) is a schematic plan view of the planetary gear, the (b) is a left side view thereof, ( c) it is a right side view. 又、図3は該遊星歯車装置の磁気的な噛み合いを説明するためのスケルトン図である。 Further, FIG. 3 is a skeleton diagram for explaining the magnetic engagement of the planetary gear set. 図において、外輪歯車4は、磁性体(例えば軟鉄材)から成る外輪盤41の外周部に、放射状磁気歯42・・・が隣り合う磁気歯間に所定の隙間を設けて、等間隔で接着等の適宜手段にて配設されている。 In the figure, the ring gear 4, the outer periphery of the outer ring plate 41 made of a magnetic material (e.g. soft iron), with a predetermined gap between the magnetic teeth radial magnetic teeth 42, ... are adjacent, adhered at equal intervals It is disposed at suitable means like. 又、該外輪盤41は、その裏面側に設けた複数個のネジ穴43・・に、ネジ77・・をネジ締めによって外輪取り付け板7に取り付けられている。 Further, the outer race plate 41, a plurality of screw holes 43 ... provided on the back side, is attached to the outer ring mounting plate 7 the screw 77 ... by screwing. この間隔は複数個のパイプ状スペーサ73・・で決められる。 This interval is determined by a plurality of pipe-shaped spacer 73 ... さらに該外輪歯車4の中心部には軸受54が圧入れており、外輪取り付け板7の中央部にネジ76でネジ止めされ軸受ホルダー71を介して、後述する太陽歯車5が回転自在に装着されている。 Further and bearing 54 is press-fitted in the center of the outer ring gear 4, via a bearing holder 71 is screwed with screws 76 to a central portion of the outer ring mounting plate 7, the sun gear 5 to be described later is rotatably mounted ing.

次に、太陽歯車5は、磁性体(例えば軟鉄材)から成る太陽盤51と、その外周部に、隣り合う磁気歯間に所定の隙間を設けて等間隔で接着等の適宜手段にて配設された放射状磁気歯52・・・と、該太陽盤51の中心部に該盤面に垂直に圧入した太陽軸53から構成され、前記取り付け板7に、前記軸受けホルダー71を介して回転自在に取り付けられている。 Then, the sun gear 5, distribution and solar panel 51 made of a magnetic material (e.g. soft iron), on its outer periphery at a suitable means such as adhesion at equal intervals with a predetermined gap between the adjacent magnetic teeth a radial magnetic teeth 52, ..., which is set, is configured from the sun shaft 53 press-fitted perpendicularly to 該盤 surface in the center of the solar panel 51, the mounting plate 7, rotatably via the bearing holder 71 It is attached. 尚、該太陽歯車5は太陽軸53に装着したセットカラー55によって、上述した外輪歯車4の磁気歯42・・・の表面と、太陽歯車5の磁気歯52・・・の表面が、ほぼ同一平面となるよう設定されている。 Incidentally, by the sun gear 5 is set collar 55 attached to the sun shaft 53, the magnetic teeth 42, ... of the surface of the ring gear 4, which has been described above, the surface of the magnetic teeth 52, ... of the sun gear 5, about the same It is set to be flat.

次に遊星歯車6は、遊星軸と一体化した遊星盤61と、その外周部に隣り合う磁気歯間に所定の隙間を設けて等間隔に接着等の適宜手段にて配設された放射状磁気歯62・・・から構成され、軸受け64を圧入した遊星歯車盤63に、該軸受け64を介して遊星軸に装着したセットカラー65によって回転自在(遊星盤の自転)に固着されている。 Then the planetary gears 6, a planet plate 61 integrated with the planetary shaft, radial magnetic disposed at suitable means such as adhesive at regular intervals with a predetermined gap between the magnetic teeth adjacent the outer periphery thereof consists tooth 62 ..., to the planetary gear plate 63 press-fitted to the bearing 64 are fixed to rotatably (rotation of the planetary Edition) by Collars 65 mounted on the planetary shaft through a shaft receptacle 64. 尚、該遊星歯車6は、遊星盤61の中心から同一円上でかつ等間隔(120°)に3個も配置されており、かつ該3個の遊星歯車6・・の各磁気歯62・・・の磁気場表面は同一平面となるよう前期セットカラー65で設定されている。 Incidentally, the planetary gear 6, three in and a on the same circle from the center of the planetary plate 61 at equal intervals (120 °) has also been arranged, and the three planetary gears 6 each magnetic tooth · 62 · magnetic field surface of ... is set in the previous year Collars 65 so as to be flush. さらに、該遊星歯車盤63は、中心部に軸受けホルダー81をネジ86でネジ止めした遊星取り付け板8に、該ホルダー81を介してセットカラー85にて回転自在(遊星盤の公転)にかつ、対向する太陽歯車5の磁気歯52・・・及び、外輪歯車4の磁気歯42・・・の表面と、遊星歯車6の磁気歯62・・・の表面とが、所定の空隙を維持して固着されている。 Further, the planetary gear plate 63, the bearing holder 81 to the planetary mounting plate 8 screwed with screws 86 to the central portion, and rotatable (revolution of the planetary Edition) by set collar 85 via the holder 81, magnetic teeth 52, ... of the sun gear 5 which faces and a magnetic tooth 42 ... of the surface of the ring gear 4, and the magnetic teeth 62, ... of the surface of the planet gear 6, while maintaining a predetermined gap It is fixed. 尚、前記外輪取り付け板7はその板面が互いに平行になるよう複数個の支柱9・・・でネジ止めにて固定されている。 Incidentally, the outer ring mounting plate 7 is fixed by screws at a plurality of struts 9 ... to the plate surface are parallel to each other. この磁気式遊星歯車装置の伝達トルクは、本装置を分解することなく該セットカラー85の取り付け位置を適時設定することで容易に可変することができる。 The transmitted torque of the magnetic type planetary gear device can be easily variable by timely setting the attachment position of the set collar 85 without disassembling the device. 尚、上述したセットカラー55、及び65は、遊星盤61の遊星軸の外周部に設けた溝にCリングを埋設して構成してもよい。 Incidentally, Collars 55 and 65, described above, may be constructed by embedding a C-ring into the groove provided on the outer periphery of the planet shaft of the planetary plate 61.

次に、回転トルクの伝達について図3を用いて説明する。 Next, will be described with reference to FIG transmission of rotational torque. 例えば太陽歯車5を駆動側とし、遊星歯車6を被駆動側とした場合、太陽歯車5の回転方向を矢印イの方向に回転させたとき、遊星歯車6は各々矢印ロの方向に自転する。 For example the sun gear 5 and the drive side, when the planetary gear 6 and the driven side, when rotating the direction of rotation of the sun gear 5 in the direction of arrow b, the planetary gear 6 rotates each in the direction of arrow b. さらに該遊星歯車6は外輪磁気歯車1との噛み合いによって矢印ハの方向に公転する。 Further planetary gear 6 revolves in the direction of arrow c by the engagement between the outer magnetic gear 1. 本発明の実施例では各々の磁気歯車の磁気歯数を、遊星歯車6を16個、太陽歯車5を32個、外輪歯車4は64個と設定しており、この場合の回転比は1対3の減速となる。 The number magnetic teeth of each of the magnetic gear in the embodiment of the present invention, 16 the planetary gear 6, a sun gear 5 to 32, ring gear 4 is set to 64 and the rotation ratio in this case is a pair the 3 of deceleration. 反対に遊星群軸より入力し、太陽軸より出力する場合は、3:1の増速となる。 Input from the planetary group axis Conversely, if the output from the sun shaft, 3: 1 speed increasing.

次に、前述した本発明の第一の実施例をもとに、本発明の別の目的である2件について詳細に説明する。 Then, based on the first embodiment of the present invention described above will be described in detail 2 is another object of the present invention. その一つは、前述した従来例では2種類の噛み合い即ち、前記外輪歯車1と遊星歯車3間、遊星歯車3と太陽歯車2間の各伝達トルクに約60%の差異があることに着目し、この両者の伝達トルクを拮抗するよう設定することで永久磁石の使用量を減らすことにある。 One of the two meshing the conventional example described above i.e., paying attention to that the between the ring gear 1 and the planetary gear 3, there is approximately 60% difference in the transmitted torque between the planetary gear 3 and the sun gear 2 is to reduce the amount of permanent magnet by setting to antagonize the transmission torque of both. もう一つの目的は、磁気的な噛み合いのモデルに改良を加えて、伝達トルクの脈動を抑えることにある。 Another object, in addition to improvements in magnetic engagement model is to suppress the pulsation of transmitted torque.

まず、前者の目的についてその解決方法を説明する。 First, the Solution for purposes of the former. 図3において、外輪歯車4の磁気歯42・・・と、これに対向し磁気的に噛み合う遊星歯車6・・の磁気歯62・・・の極性が、N極と、S極となっている有効噛み合い部2a(斜線を施した部分)で主たる伝達トルクを形成する。 3, the magnetic teeth 42, ... of the ring gear 4, the polarity of the planet gear 6 ... magnetic teeth 62 ... are meshing faces thereto magnetically, and N-pole, and has a S-pole forming a primary transmission torque effective meshing portion 2a (portion indicated by hatching). この実施例の外輪歯42・・・では、従来例の図1(イ)の外輪歯12の噛み合いの少ない外周部から削って磁気歯たけを約半分短くしたものである。 In the outer ring teeth 42, ... of this embodiment is obtained by shortening about half the magnetic tooth depth shaving from small outer periphery of the meshing of the outer ring teeth 12 of FIG conventional example 1 (b). 即ち、この有効噛み合い部2aと、後述する有効噛み合い部2b(斜線を施しは部分)の各々の噛み合い面積をほぼ同じにして伝達トルクの拮抗を図ったものである。 That is, the the effective engagement portion 2a, in which tried to antagonism of approximately the same in to the transmission torque of each of the engagement area of ​​the effective engagement portion 2b to be described later (the portion hatched). 本実施例では外輪歯の永久磁石の使用量を約半分にすることが可能となった。 It became possible to approximately half the amount of the permanent magnets of the outer ring teeth in this embodiment.

次に伝達トルクの脈動の解決方法について説明する。 It will be described resolving pulsation of transmission torque. 図1(イ)の従来例で、伝達トルクの脈動の主原因は、遊星歯車と太陽歯車の磁気的噛み合い部に起因していることが判明した。 In the conventional example of FIG. 1 (b), the main cause of pulsation of the transmitted torque, that due to the magnetic meshing portions of the planetary gear and the sun gear were found. この噛み合い部を標準的な外接噛み合い(有効噛み合い形状がラグビーボール型となっている)を、外輪歯車と遊星歯車の磁気的噛み合い部の噛み合い形状を内接噛み合い(有効噛み合いの形状が短冊状となっている)に準じた形状にすることで解決したものである。 The meshing portion meshing standard circumscribe (effective the profiles has become a rugby ball), and meshing inscribed meshing shape of the magnetic engagement of the ring gear and the planetary gear (effective meshing shape strip in which was solved with a shape conforming to going on). 即ち、外接噛み合いを内接噛み合いに近づけたものである。 That is, those closer to the meshing inscribed meshing circumscribed. この伝達トルクの脈動発生の主原因を、図を用いて詳細に説明する。 The main cause of the pulsation generation of the transmitted torque will be described in detail with reference to FIG. 図5は、前述の従来例の磁気的噛み合いを遊星磁気歯の1歯分の回転角度を4等分し、各々の噛み合い状態を示したスケルトン図で、同様に図6は本発明の実施例のそれを示したスケルトン図である。 5 shows examples of the aforementioned conventional magnetic engagement with 4 equal portions rotation angle of one tooth of the planetary magnetic teeth of the skeleton view illustrating the respective meshing, similarly 6 present invention is a skeleton diagram showing its. 図5、6の(イ)、(ロ)、(ハ)、(ニ)は遊星歯車の自転の回転角度を22.5°(360/16)の1/4づつ回転した場合の磁気的噛み合い状態を連続的に示したもので、図の点線の矢印は、磁気的な噛み合いの伝達トルクの方向を示したものである。 In FIGS (a), (b), (c), (d) magnetically engagement in the case of quarter-turn increments of 22.5 ° rotation angle of the rotation of the planetary gear (360/16) condition requiring those shown continuously, the dotted arrow in the figure shows the direction of the transmission torque of the magnetic engagement. 従来例の噛み合いではトルクの方向は遊星歯車の回転方向(自転)に対して斜めになり、回転トルクを十分に引き出せていない。 Direction than the engagement of the conventional torque becomes oblique with respect to the rotational direction of the planetary gear (rotation), not fully brought out the rotation torque. これに対して、発明例の図6では、遊星歯車の回転方向(自転)に対して、接線方向であり、伝達トルクに無駄なく作用している。 On the other hand, in FIG. 6 of the invention examples, the rotational direction of the planetary gear (rotation), a tangential, acting without waste transmitted torque. 一方、噛み合い生成開始部分(図中、点線で囲った部分)に着目すると、図5の従来例では、(イ)(ロ)は有効噛み合いの生成が主となり、又(ハ)(ニ)では、反発噛み合い(対向する磁気歯の極性が異極の状態)の生成が主になっている。 On the other hand, (in the figure, a portion surrounded by a dotted line) meshing generation start portion when focusing on, in the conventional example of FIG. 5, in (a) (ii) the effective engagement of generation becomes the main, and (c) (d) , generation of meshing repulsion (polarity opposite to the magnetic teeth of different polarity state) becomes mainly. 即ち、22.5°の回転において、この噛み合い生成開始部分が、有効噛み合いと反発噛み合いが交互に発生することが伝達トルクの脈動の主因となっている。 That is, in the rotation of 22.5 °, the meshing generation start portion, effective engagement and meshing repulsion that occurs alternately has a major cause of pulsation of the transmitted torque. これに対して、発明例では、図6の噛み合い生成開始部分(図中、点線で囲った部分)は、(イ)〜(ニ)において、ほぼ有効噛み合いと反発噛み合いが拮抗して生成されるため、回転時の伝達トルクの脈動が少なくなっている。 In contrast, in the invention examples, the meshing start generating portion of FIG. 6 (in the figure, in a portion surrounded by a dotted line) is generated by antagonizing engages rebound meshing in nearly effective (a) to (d) Therefore, pulsation of the transmission torque during rotation is low.

具体的には、太陽歯車5の磁気歯52の形状を、磁気歯の内側から放射状に形成しているところを逆放射状に形成することで、太陽歯車5の磁気歯52・・・と遊星歯車6の磁気歯62・・・の磁気的噛み合い部を、2bに示すように準内接噛み合いとすることができるが、本実施例では、太陽磁気歯の内周側と外周側を反転して形成した。 Specifically, the shape of the magnetic teeth 52 of the sun gear 5, forming a place forming radially from the inside of the magnetic teeth Conversely radially, the magnetic teeth 52, ... and the planetary gears of the sun gear 5 magnetic engagement portion of the magnetic teeth 62, ... 6, which may be meshing quasi inscribed as shown in 2b, in this embodiment, by reversing the inner and outer peripheries of the solar magnetic teeth the formed.

図4に、磁気式遊星歯車装置の伝達トルク特性を実測した結果を示す。 Figure 4 shows the result of measuring the transmission torque characteristic of a magnetic planetary gear unit. 図4(イ)は従来例の磁気式遊星歯車装置の伝達トルク特性を、図4(ロ)に本発明に係る第一の実施例の伝達トルク特性を示す。 Figure 4 (a) is a transmission torque characteristic of a magnetic planetary gear device of the conventional example, shows the transfer torque characteristics of the first embodiment according to the present invention in FIG. 4 (b). それぞれの磁気歯数は従来例では、外輪歯車の外径は200mm、太陽歯車、及び遊星歯車の外径はそれぞれ80mm、又、永久磁石には、希土類のNd−Fe―Bを使用し、磁気歯数は、遊星:太陽:外輪=24:24:96で変速比は5:1となる。 The respective magnetic teeth the conventional example, the outer diameter of the outer ring gear 200 mm, the sun gear, and each outer diameter of the planetary gear is 80 mm, also the permanent magnet is to use a Nd-Fe-B rare earth magnetic number of teeth is the planet: sun: outer ring = 24: 24: 96 in the gear ratio is 5: 1. 一方、本発明の実施例では、外輪歯車、太陽歯車、遊星歯車の外径はそれぞれ、180mm、100mm、68mm、で、永久磁石は、同様にNd−Fe―Bを使用した。 On the other hand, in the embodiment of the present invention, the outer ring gear, the sun gear, each outer diameter of the planetary gear is 180 mm, 100 mm, 68mm in, the permanent magnet used was Nd-Fe-B as well. 又、磁気歯数は、遊星:太陽:外輪=24:48:96で変速比は3:1とした。 The magnetic teeth are planetary: Solar: outer ring = 24: 48: 96 in the gear ratio is 3: 1. グラフに示すように本発明の実施例では伝達トルクの脈動が、従来例に対して約32%に減少した。 Pulsation of transmitted torque in the embodiment of the present invention as shown in the graph, was reduced to about 32% with respect to the prior art.

次に伝達トルクの向上を目的とした本発明の第二の実施例について説明する。 Next will be described a second embodiment of the present invention for the purpose of improving the transmission torque. 前述したように、一般的に磁気式遊星歯車の伝達トルクは、遊星歯車と太陽歯車間の伝達トルクが、外輪歯車と遊星歯車間の伝達トルクに対し約60%であり、40%低くなっている。 As described above, the transmission torque of the general magnetic planet gears, the transmission torque between the planetary gear and the sun gear, to transfer torque between the ring gear and the planetary gear is about 60%, is 40% lower there. 本発明の骨子は、太陽歯車を2個用いて、この遊星歯車と太陽歯車間の伝達トルクを強くすることにより、遊星歯車装置としての伝達トルクを向上する方法を提案するものである。 Gist of the present invention uses two sun gears, by strongly transmission torque between the planetary gear and the sun gear, it proposes a method of improving the transmission torque of the planetary gear device. 図7は本発明による第二の実施例の磁気式遊星歯車装置の概略を示した一部断面を含む平面図である。 Figure 7 is a plan view in partial cross-section showing an outline of a magnetic planetary gear device of the second embodiment according to the present invention. 図において、4aは外周部に磁気歯42aを配設した外輪歯車、6aは、遊星盤61aの外周部の表裏に磁気歯62a・・・、及び磁気歯63a・・・を配設した遊星歯車である。 In the figure, the outer ring gear 4a is which is disposed a magnetic teeth 42a on the outer peripheral portion, 6a is a planetary gear which is disposed a magnetic teeth 62a · · ·, and the magnetic teeth 63a · · · in the front and back sides of the outer peripheral portion of the planetary plate 61a it is. ここで該磁気歯62a・・・は前記外輪歯車4aの磁気歯42a・・・と対向して磁気的な噛み合いを形成するが、磁気歯63aは外輪歯42aと磁気的に噛み合わない。 Here magnetic KIHA 62a · · · is to form a magnetic engagement faces the magnetic teeth 42a · · · of the ring gear 4a, the magnetic teeth 63a is not magnetically engaged with the outer ring teeth 42a. 又5a、5bは、その外周部に磁気歯52a・・・、及び磁気歯52b・・・を配設した太陽歯車であって、該磁気歯52a、磁気歯52bはそれぞれ前記遊星歯車6aの表裏の磁気歯62a・・・と対向して配置され、磁気的な噛み合いを形成する。 Also 5a, 5b, the magnetic teeth 52a · · · in the outer periphery thereof, and a sun gear which is disposed a magnetic teeth 52b · · ·, front and back of each magnetic KIHA 52a, the magnetic teeth 52b are the planetary gears 6a disposed of magnetic teeth 62a · · · and opposite to, to form a magnetic engagement. 即ち、遊星歯車と太陽歯車の磁気的噛み合いが、前述した本発明の第一の実施例に対し倍加させたことにより、磁気式遊星歯車装置としての伝達トルクを1.8倍に向上させたものである。 That is, the engagement magnetically planetary gear and the sun gear, which by was doubled to the first embodiment of the present invention described above, improved the transmission torque of the magnetic planetary gearing to 1.8 times it is.

又、図8は、前述の伝達トルク向上方法に対して、磁気歯の削減した改善例を示す第三の実施例の概略を示した一部断面を含む平面図である。 Further, FIG. 8 is a plan view including relative transmission torque enhancing method described above, a partial section showing an outline of a third embodiment showing an improved example of reduction of the magnetic tooth. 前述の第二の実施例と異なる点は、遊星歯車6bの遊星盤61bに配設された磁気歯の62b・・・の表裏の磁気歯面が、太陽歯車5a、及び5bの各磁気歯52a、52bと噛み合いうよう構成したもので、これによって太陽歯の磁気歯を増やすことなく磁気式歯車装置の伝達トルクを強くしたものである。 Foregoing second embodiment differs from the magnetic tooth surfaces of the front and back of 62b · ​​· · of magnetic teeth arranged on the planetary plate 61b of the planetary gear 6b ​​is, each magnetic tooth 52a of the sun gear 5a, and 5b , which was constructed so that might mesh with 52 b, whereby is obtained by strongly transmission torque of the magnetic gearing without increasing the magnetic teeth of the sun teeth.

以上説明した遊星歯車、太陽歯車、外輪歯車の磁気歯は、それぞれ3種類の磁気歯の内周側幅は、有効噛み合い部を極力多くするためほぼ同じ幅としており、又、磁気歯の数は、何れもN極、S極が同数を基本とする。 Above-described planetary gear, the sun gear, the magnetic teeth of the outer ring gear, the inner circumferential side width of each three magnetic teeth are made substantially the same width to as much as possible the effective engagement portion, and the number of magnetic teeth both N-pole, S pole is basically the same number. 尚、本発明の実施例では、便宜上遊星歯車を3個用いた例で説明したが、遊星歯車数が複数であれば本発明の及ぶところである。 In the embodiment of the present invention, for convenience has been described an example using three planetary gears, is where the number of the planetary gear over which the present invention as long as it is plural. さらに、本発明では磁気歯の材質は、Nd、Fe、B系の高エネルギー積を有する希土類磁石を使用したが、エネルギーの小さい他の磁性材を用いても、本発明の及ぶところである。 Further, the material of the magnetic teeth in the present invention, Nd, Fe, was used a rare earth magnet having high energy product B system, even with a small addition of the magnetic material having energy, is where the reach of the present invention.

従来の磁気式遊星歯車装置の概略平面図及び、伝達トルクのシステム図 Schematic plan view of a conventional magnetic planetary gear unit and a system diagram of a transmission torque 本発明による第一、及び第二の実施例の概略平面図、及び側面図 First, and schematic plan view of a second embodiment according to the present invention, and a side view 同実施例の伝達トルクシステム図 Transmission torque system diagram of the embodiment 磁気式遊星歯車装置の伝達トルク特性図 Transmission torque characteristic diagram of a magnetic planetary gear unit 従来の磁気式遊星歯車の磁気的噛み合い状態の詳細図 Detailed view of the magnetic meshing of a conventional magnetic planetary gear 本発明による第一の実施例の磁気的噛み合い状態の詳細図 Detailed view of the magnetic meshing of the first preferred embodiment of the present invention 本発明によるの第二の実施例の概略正面図 Schematic front view of a second embodiment of the present invention 本発明によるの第三の実施例の概略正面図 Schematic front view of a third embodiment of the present invention

符号の説明 DESCRIPTION OF SYMBOLS

1、4、4a、4b 磁気式外輪歯車2、5、5a、5b 磁気式太陽歯車3、6、6a、6b 磁気式遊星歯車7 外輪歯車取り付け板8 遊星取り付け板9 スペーサー11外輪盤12、42、42a、42b 外輪磁気歯21、51、51a、太陽盤22、52、52a、52b 太陽磁気歯31、61、61a、遊星盤32、62、62a、63a、62b 遊星磁気歯23、53 太陽軸24、34、54、64、 軸受25、33、65、85 セットカラー35、63 遊星歯車盤36、66 遊星軸72、76,77、86 ネジ43 ワッシャ71、81 軸受ホルダー : Synthesis of 1,4,4, 4b magnetic ring gear 2,5,5a, 5b magnetic sun gear 3,6,6a, 6b magnetic planetary gear 7 ring gear mounting plate 8 planetary mounting plate 9 spacer 11 outer panel 12, 42 , 42a, 42b outer magnetic teeth 21,51,51A, solar panel 22,52,52a, 52b solar magnetic teeth 31,61,61A, planetary Release 32,62,62a, 63a, 62b planetary magnetic teeth 23 and 53 sun shaft 24,34,54,64, bearing 25,33,65,85 Collars 35,63 planetary gear Release 36,66 planetary shafts 72,76,77,86 screws 43 washers 71, 81 bearing holder

Claims (4)

  1. 磁気式太陽歯車と、複数個の磁気式遊星歯車と、1個の磁気式外輪歯車から構成され、各々の対向する該磁気歯車間に所定の空隙を設け、動力伝達には磁気の反発力及び、吸引力を利用して、非接触で動力伝達させる磁気式遊星歯車装置(以下磁気式遊星歯車装置と略記する)において、磁気歯車間の空隙を、所望の伝達トルクに応じて装置を分解することなく調整可能な構造としたことを特徴とする磁気式遊星歯車装置。 A magnetic sun gear, a plurality of magnetic planetary gear, is composed of one magnetic ring gear, it is provided a predetermined gap between the magnetic gears opposing each magnetic repulsion and the power transmission decomposed by utilizing the suction force, the magnetic planetary gear device for power transmission in a non-contact (hereinafter referred to as magnetic planetary gear device), the gap between the magnetic gears, the device according to the desired transmission torque magnetic planetary gear unit being characterized in that the adjustable structure without.
  2. 磁気式遊星歯車装置において、遊星歯車と太陽歯車、及び遊星歯車と外輪歯車の各々の伝達トルクが、ほぼ同トルクとなるよう外輪歯車の磁気歯たけを短くしたことを特徴とする磁気式遊星歯車装置。 In magnetic planetary gear device, a magnetic planetary gear, wherein the planetary gear and the sun gear, and each of the transmission torque of the planetary gear and ring gear has a shorter magnetic tooth depth of the outer ring gear so as to be substantially the same torque apparatus.
  3. 磁気式遊星歯車装置において、遊星歯車と太陽歯車の主たる磁気的噛み合い部分を、内接噛み合い方式となるよう太陽歯車の磁気歯形状を形成したことを特徴とする磁気式遊星歯車装置。 In magnetic planetary gear device, magnetic planetary gear unit, characterized in that the principal magnetic meshing portions of the planetary gear and the sun gear to form a magnetic tooth shape of the sun gear so as to be inscribed meshing type.
  4. 磁気式遊星歯車装置において、太陽歯車を2個設けて伝達トルクを強くしたことを特徴とする磁気式遊星歯車装置。 In magnetic planetary gear device, magnetic planetary gear apparatus characterized by strongly transmitted torque sun gear 2 provided.
JP2004269888A 2003-09-19 2004-09-16 Magnetic planetary gear unit Active JP3942102B2 (en)

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Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2006105617A1 (en) * 2005-04-08 2006-10-12 Andrew Boyd French Magnetic drive apparatus
JP2009250358A (en) * 2008-04-07 2009-10-29 Sumitomo Heavy Ind Ltd Magnetic gear reduction gear
US7687956B2 (en) 2003-01-17 2010-03-30 Magnetic Torque International, Ltd. Drive motor system
WO2012044791A1 (en) * 2010-09-29 2012-04-05 David Chi-Henry Su Magnetic levitation transmission
US20120242089A1 (en) * 2011-03-23 2012-09-27 National Formosa University Energy transforming apparatus

Cited By (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US7687956B2 (en) 2003-01-17 2010-03-30 Magnetic Torque International, Ltd. Drive motor system
WO2006105617A1 (en) * 2005-04-08 2006-10-12 Andrew Boyd French Magnetic drive apparatus
JP2009250358A (en) * 2008-04-07 2009-10-29 Sumitomo Heavy Ind Ltd Magnetic gear reduction gear
WO2012044791A1 (en) * 2010-09-29 2012-04-05 David Chi-Henry Su Magnetic levitation transmission
US20120242089A1 (en) * 2011-03-23 2012-09-27 National Formosa University Energy transforming apparatus
US8581461B2 (en) * 2011-03-23 2013-11-12 National Formosa University Energy transforming apparatus

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