JP2012041971A - Step-up gear - Google Patents

Step-up gear Download PDF

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JP2012041971A
JP2012041971A JP2010183202A JP2010183202A JP2012041971A JP 2012041971 A JP2012041971 A JP 2012041971A JP 2010183202 A JP2010183202 A JP 2010183202A JP 2010183202 A JP2010183202 A JP 2010183202A JP 2012041971 A JP2012041971 A JP 2012041971A
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gear
main shaft
intermediate transmission
inner main
occlusal
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JP5167318B2 (en
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Makoto Minezaki
眞 峯崎
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MINE SERVICE KK
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    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

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Abstract

PROBLEM TO BE SOLVED: To provide a step-up gear capable of obtaining a high output at low-speed rotation.SOLUTION: The step-up gear includes an outer driving gear 1 which receives energy and rotates and an inner main shaft gear 2 which transmits a rotative force of the outer driving gear to a rotator, wherein intermediate transmission gears 3A, 3B are arranged between the outer driving gear and the inner driving main shaft gear so as to be capable of biting the outer driving gear 1 and the inner main shaft gear 2, the rotative force of the outer driving gear is stepped up with the intermediate transmission gear and the inner main shaft gear and the rotator is caused to rotate with a stepped-up output. The respective gears are formed in ring shapes having diameters different from each other, respectively have biting face and non-biting face on the opposite inner peripheral and outer circumferential faces of respective gears, teeth parts 5, 9a, 9b, 11a, 11b, 12 which assume wave shapes are formed on opposite biting faces by every gear, the biting state of respective opposite teeth parts is provided, the rotative force of the outer driving gear is transmitted to the inner main shaft gear via respective teeth parts, at the same time, guide rollers 13, 14, 15 are inserted between the opposed non-biting faces of respective gears and the opposed teeth parts are bitten with each other in the pressing direction of a guide roller.

Description

本発明は、例えば、風力発電・水力発電、電気自動車、送風機などにおいて、回転力を増速するために使用される増速機に関し、詳しくは、独特の波形状を呈するギヤを用いた増速機に関するものである。   The present invention relates to a speed increaser that is used to increase rotational force in, for example, wind power generation / hydropower generation, electric vehicles, blowers, and the like, and more particularly, speed increase using a gear that exhibits a unique wave shape. Related to the machine.

近年、二酸化炭素の削減などにより地球環境を改善することを目的として、自然エネルギーを利用した風力発電や水力発電が注目されている。   In recent years, wind power generation and hydroelectric power generation using natural energy have attracted attention for the purpose of improving the global environment by reducing carbon dioxide.

そして、風力発電は、風の運動エネルギーを利用してブレードを回転させて、発電機を回転駆動させるものであるが、通常は、多軸歯車式や遊星歯車式の増速機を用いて回転を増速している。又、水力発電は、水の運動エネルギーを利用して水車を回転させて、発電機を回転駆動させるものであるが、やはり、同様な増速機を用いて回転を増速している。   In wind power generation, the blades are rotated using the kinetic energy of the wind to drive the generator. Usually, it is rotated using a multi-shaft gear type or planetary gear type gearbox. The speed is increased. Hydroelectric power generation uses a kinetic energy of water to rotate a water turbine to drive a generator. However, a similar speed increaser is used to increase the rotation speed.

しかし、風力発電の出力を増力するためには、ブレードの回転速度を高速にする必要があるが、これを都心や住宅街などで行なうと、増速機部分で大きな機械音が発生するので、騒音問題が発生する恐れがあり、又、水力発電でも、多くの電力を発電させるためには、河川の水量や勢いが必要となる。   However, in order to increase the output of wind power generation, it is necessary to increase the rotation speed of the blade, but if this is done in the city center or residential area, a large mechanical noise will be generated in the speed increaser part, There is a risk of noise problems, and hydroelectric power generation requires river water volume and momentum to generate a large amount of power.

本発明は、斯かる従来の実情に鑑み開発されたもので、請求項１記載の発明は、エネルギーを受けて回転する外側駆動ギヤと、該外側駆動ギヤの回転力を回転体に伝える内側主軸ギヤとを備え、上記外側駆動ギヤと内側主軸ギヤとの間に複数の中間伝達ギヤを咬合可能に配設し、外側駆動ギヤの回転力を上記各中間伝達ギヤと内側主軸ギヤとで増速して、上記回転体を該増速された回転出力で回転させる増速機であって、上記各ギヤは、径の異なるリング状に成形されて、各ギヤの対向する内・外周面に咬合面と非咬合面とを有し、各ギヤごとで対向する咬合面に波形状を呈する歯部を連続して形成し、該対向する各波形状の歯部の面接触による咬合状態を得て、外側駆動ギヤの回転力を各波形状の歯部を介して内側主軸ギヤに伝達すると共に、各ギヤの上記対向する非咬合面間にガイドローラーを介設して、該ガイドローラーの押圧方向において対向する波形状の歯部同士を咬合させることを特徴とする。   The present invention has been developed in view of such a conventional situation, and the invention according to claim 1 is directed to an outer drive gear that rotates by receiving energy, and an inner main shaft that transmits a rotational force of the outer drive gear to a rotating body. A plurality of intermediate transmission gears that can be engaged between the outer drive gear and the inner main shaft gear, and the rotational force of the outer drive gear is increased by the intermediate transmission gear and the inner main shaft gear. The speed increasing device for rotating the rotating body with the increased rotational output, wherein each gear is formed in a ring shape having different diameters and meshes with the inner and outer peripheral surfaces facing each gear. A tooth portion having a surface and a non-occlusal surface is formed continuously on each occlusal surface facing each gear, and an occlusal state is obtained by surface contact of each tooth portion facing each other. When the rotational force of the outer drive gear is transmitted to the inner main shaft gear via the corrugated teeth, , And interposed a guide roller between the non-occlusal surface of the opposing gears, characterized in that to bite the corrugated toothing facing each other in the pressing direction of the guide rollers.

請求項２記載の発明は、請求項１を前提として、各ギヤの対向する咬合面間に波形状の歯部と相似する滑り止めリングを組み込んだことを特徴とする。   According to a second aspect of the present invention, on the premise of the first aspect, a non-slip ring similar to a wave-shaped tooth portion is incorporated between the opposing occlusal surfaces of the respective gears.

請求項３記載の発明は、請求項１乃至請求項２を前提として、各ギヤの非咬合面間に介設されるガイドローラーは、内・外の各段ごとで、介設位置が交互に逆向きとなっていることを特徴とする。   The invention according to claim 3 is based on claims 1 and 2, and the guide rollers interposed between the non-occlusion surfaces of the gears are alternately arranged at the inner and outer stages. It is characterized by being reversed.

請求項４記載の発明は、請求項１乃至請求項３を前提として、各ギヤの咬合面と非咬合面の境にギヤのブレ防止手段を設けたことを特徴とする。   According to a fourth aspect of the present invention, on the premise of the first to third aspects, a gear anti-shake means is provided at the boundary between the occlusal surface and the non-occlusal surface of each gear.

依って、請求項１記載の発明にあっては、外側の駆動ギヤから中間の伝達ギヤを経て内側の主軸ギヤへ回転力を伝える過程で、各ギヤの対向する波形状の歯部が面接触状態をもって咬合して回転力を伝達するので、従来のものと比べると、接触面積が多く且つ伝達面も数箇所と多くなって、回転力を分散して伝えることが可能となる。この為、例え、最初の外側駆動ギヤが受ける回転力が少なくとも、その回転力が内部に配されて徐々に径が小さくなっていく各中間伝達ギヤと内側主軸ギヤに伝達されて増速するので、発電機などの回転体をこの増速された回転出力で回転させられる。   Therefore, according to the first aspect of the present invention, in the process of transmitting the rotational force from the outer drive gear to the inner main shaft gear through the intermediate transmission gear, the opposing wavy tooth portions of each gear are in surface contact. Since the rotational force is transmitted by being occluded in a state, the contact area is larger and the transmission surface is increased to several places as compared with the conventional one, and the rotational force can be distributed and transmitted. For this reason, for example, the rotational force received by the first outer drive gear is at least transmitted to the intermediate transmission gear and the inner main shaft gear that are gradually reduced in diameter as the rotational force is arranged inside, so that the speed increases. A rotating body such as a generator can be rotated with the increased rotational output.

又、各ギヤは回転しながら、面から面へと接触することとなるので、騒音や振動を効果的に抑えることができる。   Moreover, since each gear rotates and contacts from surface to surface, noise and vibration can be effectively suppressed.

請求項２記載の発明にあっては、各ギヤの対向する咬合面間に滑り止めリングを組み込んだので、軽い力で高速回転して、騒音問題を確実に防止することが可能となる。   In the invention according to claim 2, since the non-slip ring is incorporated between the occlusal surfaces facing each gear, it is possible to rotate at a high speed with a light force and reliably prevent noise problems.

請求項３記載の発明にあっては、ガイドローラーは内・外の各段ごとで介設位置が交互に逆向きとなっているので、力を伝える箇所を集中させずに分散させて、力を増速し安定した回転を保障できる。   In the invention according to claim 3, since the guide roller is alternately reversed in each of the inner and outer steps, the guide roller is dispersed without concentrating the portion transmitting the force. The speed can be increased to ensure stable rotation.

請求項４記載の発明にあっては、各ギヤの咬合面と非咬合面の境にブレ防止手段を設けたので、回転して回転数を増した時に、各ギヤのブレや振動を抑えて、安定した回転が保障できる。   In the invention according to claim 4, since the anti-shake means is provided at the boundary between the occlusal surface and the non-occlusal surface of each gear, when the rotational speed is increased by rotating, the vibration and vibration of each gear are suppressed. Can ensure stable rotation.

本発明の実施例に係る増速機の原理を示す概略図である。It is the schematic which shows the principle of the gearbox which concerns on the Example of this invention. 同増速機を断面して示す概略図である。It is the schematic which shows the same speed increaser in cross section. 各ギヤの波形状の歯部とガイドローラーの関係を示す説明図である。It is explanatory drawing which shows the relationship between the wave-shaped tooth | gear part of each gear, and a guide roller. 外側駆動ギヤと第一中間伝達ギヤと第一ガイドローラーの関係を説明する要部説明図である。It is principal part explanatory drawing explaining the relationship between an outer side drive gear, a 1st intermediate transmission gear, and a 1st guide roller. 増速機が使用される発電機を示す要部断面図である。It is principal part sectional drawing which shows the generator in which a gearbox is used. 同発電機を別の方向から示す要部断面図である。It is principal part sectional drawing which shows the generator from another direction. （Ａ）は内側主軸ギヤの停止時における永久磁石とコイル巻線の関係を示す要部断面図、（Ｂ）は内側主軸ギヤの起動時における永久磁石とコイル巻線の関係を示す要部断面図である。(A) is a principal part sectional view showing the relationship between the permanent magnet and the coil winding when the inner spindle gear is stopped, and (B) is a principal part sectional view showing the relationship between the permanent magnet and the coil winding when starting the inner spindle gear. FIG. 外側駆動ギヤと第一中間伝達ギヤの咬合状態を説明する要部拡大説明図である。It is a principal part expanded explanatory view explaining the occlusion state of an outer side drive gear and a 1st intermediate | middle transmission gear.

本発明は、エネルギーを受けて回転する外側駆動ギヤと、該外側駆動ギヤの回転力を回転体に伝える内側主軸ギヤとを備え、上記外側駆動ギヤと内側主軸ギヤとの間に複数の中間伝達ギヤを咬合可能に配設し、外側駆動ギヤの回転力を上記各中間伝達ギヤと内側主軸ギヤとで増速して、上記回転体を該増速された回転出力で回転させる増速機を前提として、上記各ギヤは、径の異なるリング状に成形されて、各ギヤの対向する内・外周面に咬合面と非咬合面とを有し、各ギヤごとで対向する咬合面に波形状を呈する歯部を連続して形成し、該対向する各波形状の歯部の面接触による咬合状態を得て、外側駆動ギヤの回転力を各波形状の歯部を介して内側主軸ギヤに伝達すると共に、各ギヤの上記対向する非咬合面間にガイドローラーを介設して、該ガイドローラーの押圧方向において対向する波形状の歯部同士を咬合させることにより、低速回転で高出力を得んとするものである。   The present invention includes an outer drive gear that rotates by receiving energy, and an inner main shaft gear that transmits a rotational force of the outer drive gear to a rotating body, and a plurality of intermediate transmissions between the outer drive gear and the inner main shaft gear. A speed increasing device that disposes the gears so as to be able to engage with each other, increases the rotational force of the outer drive gear with the intermediate transmission gears and the inner main shaft gear, and rotates the rotating body with the increased rotational output. As a premise, each gear is formed in a ring shape having a different diameter, has an occlusal surface and a non-occlusion surface on the inner and outer peripheral surfaces facing each gear, and has a wave shape on the occlusal surface facing each gear. The tooth portions exhibiting the following are formed continuously, the occlusal state is obtained by the surface contact of the respective corrugated tooth portions facing each other, and the rotational force of the outer drive gear is applied to the inner main shaft gear via the corrugated tooth portions. And a guide roller is interposed between the opposing non-occlusion surfaces of each gear. , By occlusion of the corrugated toothing facing each other in the pressing direction of the guide rollers, it is an ¥ high output in low-speed rotation.

以下、本発明を図示する好適な実施例に基づいて詳述すれば、該実施例に係る増速機は、風力や水力の発電機用として開発されたもので、図１・図２に示す如く、風や水の運動エネルギーを受けて回転する１枚の外側駆動ギヤ１と、後述する発電機２２側に連結されて増速された回転出力で発電機２２を回転させる１枚の内側主軸ギヤ２と、該外側駆動ギヤ１と内側主軸ギヤ２との間に咬合可能に配設される２枚の中間伝達ギヤ３Ａ・３Ｂとを備え、各ギヤ１・３Ａ・３Ｂ・２は、外側から内側に向かって、径が順に小径（７０％）となるリング状を呈している。尚、具体的には図示しないが、外側駆動ギヤ１の外周には、風力の場合は複数のブレードを、水力の場合は水車を直接又は外枠などを介して一体的に取り付けるものとする。   Hereinafter, the present invention will be described in detail with reference to the preferred embodiments shown in the drawings. The speed increaser according to the embodiments has been developed for wind power or hydraulic power generators and is shown in FIGS. 1 and 2. As described above, one outer drive gear 1 that rotates by receiving the kinetic energy of wind and water, and one inner main shaft that rotates the generator 22 with a rotational output increased in speed and connected to the generator 22 side described later. A gear 2 and two intermediate transmission gears 3A and 3B disposed so as to be able to be engaged between the outer drive gear 1 and the inner main shaft gear 2 are provided. The gears 1, 3A, 3B, and 2 From the inside toward the inside, it has a ring shape whose diameter becomes smaller (70%) in order. Although not specifically shown, a plurality of blades are attached to the outer periphery of the outer drive gear 1 in the case of wind power, and a water turbine is attached directly or via an outer frame in the case of hydraulic power.

そして、上記の各ギヤに関しては、図３・図４に示す如く、外側駆動ギヤ１に対しては、その内周面のみに咬合面４ａと非咬合面４ｂとを平行に連続して画成して、前者の咬合面４ａに緩やかな曲線を呈する波形状の歯部５を連続して形成し、後者の非咬合面４ｂに後述する第一ガイドローラー１３の案内溝６を連続して形成する構成となっている。   As shown in FIGS. 3 and 4, with respect to each of the gears described above, the outer drive gear 1 is continuously defined with the occlusal surface 4a and the non-occlusion surface 4b in parallel only on the inner peripheral surface thereof. Then, a wave-shaped tooth portion 5 having a gentle curve is continuously formed on the former occlusal surface 4a, and a guide groove 6 of a first guide roller 13 to be described later is continuously formed on the latter non-occlusal surface 4b. It is the composition to do.

又、２枚の各中間伝達ギヤ３Ａ・３Ｂ中、第一中間伝達ギヤ３Ａに対しては、図示する如く、その内・外周面に咬合面７ａ・８ａと非咬合面７ｂ・８ｂとを平行に連続して画成して、内・外の各咬合面７ａ・８ａに上記の波形状の歯部９ａ・９ｂを連続して形成し、内・外の各非咬合面７ｂ・８ｂに後述する第一ガイドローラー１３と第二ガイドローラー１４の案内溝１０ａ・１０ｂを連続して形成し、第二中間伝達ギヤ３Ｂに対しては、具体的には図示しないが、第一中間伝達ギヤ３Ａと同様に、その内・外周面に咬合面と非咬合面とを平行に連続して画成して、内・外の各咬合面に上記の波形状の歯部１１ａ・１１ｂを連続して形成し、内・外の各非咬合面に後述する第二ガイドローラー１４と第三ガイドローラー１５の案内溝を連続して形成する構成となっている。   Of the two intermediate transmission gears 3A and 3B, the first intermediate transmission gear 3A has an occlusal surface 7a and 8a and an unoccluded surface 7b and 8b parallel to the inner and outer peripheral surfaces as shown in the figure. The above-mentioned corrugated teeth 9a and 9b are continuously formed on the inner and outer occlusal surfaces 7a and 8a, and the inner and outer non-occlusal surfaces 7b and 8b are described later. The guide grooves 10a and 10b of the first guide roller 13 and the second guide roller 14 are continuously formed, and although not specifically shown for the second intermediate transmission gear 3B, the first intermediate transmission gear 3A Similarly, the occlusal surface and the non-occlusal surface are continuously defined in parallel on the inner and outer peripheral surfaces, and the above-described wave-shaped tooth portions 11a and 11b are continuously formed on the inner and outer occlusal surfaces. The guide groove of the 2nd guide roller 14 and the 3rd guide roller 15 which are formed, and is mentioned later on each inside / outside non-occlusion surface is continued. And has a configuration to be formed.

最後の内側主軸ギヤ２に対しては、その外周面のみに同様な咬合面（図示せず）と非咬合面（図示せず）とを平行に連続して画成して、咬合面に上記の波形状の歯部１２を連続して形成し、非咬合面に後述する第三ガイドローラー１５の案内溝（図示せず）を連続して形成する構成となっている。尚、図４の（ａ）・（ｂ）・（ｃ）・（ｄ）は、図３の（ａ）・（ｂ）・（ｃ）・（ｄ）の対応する箇所を断面したものである。   For the final inner main shaft gear 2, a similar occlusal surface (not shown) and a non-occlusion surface (not shown) are continuously defined in parallel only on the outer peripheral surface thereof, The wavy tooth portion 12 is continuously formed, and a guide groove (not shown) of a third guide roller 15 to be described later is continuously formed on the non-occlusion surface. 4 (a), (b), (c), and (d) are cross-sectional views corresponding to (a), (b), (c), and (d) in FIG. .

従って、外側駆動ギヤ１の内周咬合面４ａに形成された歯部５と第一中間伝達ギヤ３Ａの外周咬合面７ａに形成された歯部９ａとが咬合し、該第一中間伝達ギヤ３Ａの内周咬合面８ａに形成された歯部９ｂと第二中間伝達ギヤ３Ｂの外周咬合面に形成された歯部１１ａとが咬合し、該第二中間伝達ギヤ３Ｂの内周咬合面に形成された歯部１１ｂと内側主軸ギヤ２の外周咬合面に形成された歯部１２とが咬合して、回転力を増速することとなる。   Accordingly, the tooth portion 5 formed on the inner peripheral occlusal surface 4a of the outer drive gear 1 and the tooth portion 9a formed on the outer peripheral occlusal surface 7a of the first intermediate transmission gear 3A are engaged, and the first intermediate transmission gear 3A. The tooth portion 9b formed on the inner peripheral occlusal surface 8a and the tooth portion 11a formed on the outer peripheral occlusal surface of the second intermediate transmission gear 3B are engaged with each other and formed on the inner peripheral occlusal surface of the second intermediate transmission gear 3B. The tooth portion 11b thus formed and the tooth portion 12 formed on the outer peripheral occlusion surface of the inner main shaft gear 2 are engaged with each other to increase the rotational force.

しかし、これら各ギヤ１・３Ａ・３Ｂ・２は、既述した如く、径が７０％と順に小径となって、その全周において歯部同士が全体で咬合することができないので、本実施例にあっては、上記した外側駆動ギヤ１の内周非咬合面４ｂに形成された案内溝６と第一中間伝達ギヤ３Ａの外周非咬合面７ｂに形成された案内溝１０ａ間に第一ガイドローラー１３を回転可能に介設し、該第一中間伝達ギヤ３Ａの内周非咬合面８ｂに形成された案内溝１０ｂと第二中間伝達ギヤ３Ｂの外周非咬合面に形成された案内溝間に第二ガイドローラー１４を回転可能に介設し、該第二中間伝達ギヤ３Ｂの内周非咬合面に形成された案内溝と内側主軸ギヤ２の外周非咬合面に形成された案内溝間に第三ガイドローラー１５を回転可能に介設して、各ガイドローラー１３・１４・１５の押圧方向において対向する波形状の歯部５・９ａ、９ｂ・１１ａ、１１ｂ・１２同士をその一部において咬合させる構成となっている。   However, as described above, the gears 1, 3 A, 3 B, and 2 have a diameter of 70% in order, and the tooth portions cannot be engaged with each other over the entire circumference. In this case, the first guide is between the guide groove 6 formed on the inner peripheral non-engagement surface 4b of the outer drive gear 1 and the guide groove 10a formed on the outer peripheral non-engagement surface 7b of the first intermediate transmission gear 3A. A roller 13 is interposed between the guide groove 10b formed on the inner peripheral non-engagement surface 8b of the first intermediate transmission gear 3A and the guide groove formed on the outer peripheral non-engagement surface of the second intermediate transmission gear 3B. A second guide roller 14 is rotatably interposed between the guide groove formed on the inner peripheral non-engagement surface of the second intermediate transmission gear 3B and the guide groove formed on the outer peripheral non-engagement surface of the inner main shaft gear 2. Each guide roller is provided with a third guide roller 15 rotatably. 3, 14, 15 corrugated toothing 5-9a facing in the pressing direction of, 9b-11a, and has a configuration to bite at a portion thereof 11b-12 to each other.

尚、各段のガイドローラー１３・１４・１５は、ギヤ１・３Ａ・３Ｂ・２同士の間隔に応じてその径が決定されることとなるが、約１２０°の開いた角度の中に３個づつ連結腕１６を介して連結され、且つ、夫々のガイドローラー１３・１４・１５全体は共通の保持金具１７を介して一体的に固定され、内・外の各段ごとで、その介設位置が交互に逆向きとなっている。従って、径の異なる各ギヤ１・３Ａ・３Ｂ・２同士がスムーズに安定した回転が可能となる。   The diameters of the guide rollers 13, 14, 15 at each stage are determined according to the distance between the gears 1, 3 A, 3 B, 2, but the guide rollers 13, 14, 15 are 3 in an open angle of about 120 °. The guide rollers 13, 14, 15 are connected to each other individually via a connecting arm 16, and are integrally fixed to each other via a common holding bracket 17. The positions are alternately reversed. Accordingly, the gears 1, 3A, 3B, and 2 having different diameters can smoothly and stably rotate.

即ち、外側駆動ギヤ１の力を第一中間伝達ギヤ３Ａへ、該第一中間伝達ギヤ３Ａから第二中間伝達ギヤ３Ｂへと回転力を伝達する際に、ガイドローラーの反対側の歯部同士が咬合して力を伝達するため、ガイドローラーを一方向に集中させて取り付けた場合のように、力を伝える位置が（咬合位置）が片側に集中することがない。従って、全体の重心を中央にもって来るために、夫々のガイドローラー１３・１４・１５を交互に介設した訳である。   That is, when transmitting the rotational force of the outer drive gear 1 to the first intermediate transmission gear 3A and from the first intermediate transmission gear 3A to the second intermediate transmission gear 3B, the teeth on the opposite side of the guide roller Since the occlusal bite transmits the force, the position where the force is transmitted (the occlusal position) does not concentrate on one side as in the case where the guide roller is concentrated and attached in one direction. Therefore, in order to bring the entire center of gravity to the center, the guide rollers 13, 14, and 15 are alternately provided.

更に、本実施例にあっては、上記した各ギヤ１・３Ａ・３Ｂ・２の対向する咬合面間に波形状の歯部５・９ａ・９ｂ・１１ａ・１１ｂ・１２と相似する形状のラバーから成る滑り止めリング１８を組み込んで、騒音問題を防止する構成を併せて採用している（図８参照）。   Further, in the present embodiment, the rubber having a shape similar to the wave-shaped tooth portions 5, 9a, 9b, 11a, 11b, and 12 between the facing occlusal surfaces of the gears 1, 3A, 3B, and 2 described above. The structure which prevents the noise problem by incorporating the non-slip ring 18 made of is also employed (see FIG. 8).

これに加えて、図４に示す如く、各ギヤ１・３Ａ・３Ｂ・２の咬合面と非咬合面の境に凹凸嵌合方式のズレ防止手段１９ａ・１９ｂを形成して、回転して回転数を増した時に、各ギヤ１・３Ａ・３Ｂ・２のブレや振動を効果的に抑えて、安定した回転が保障できる構成をも併せて採用している。尚、ブレ防止手段１９ａ・１９ｂに関しては、外側駆動ギヤ１と第一中間伝達ギヤ３Ａのみしか図示してないが、第二中間伝達ギヤ３Ｂや内側主軸ギヤ２にも同様に設けるものとする。   In addition to this, as shown in FIG. 4, uneven engagement type displacement prevention means 19 a, 19 b are formed at the boundary between the occlusal surface and the non-occlusion surface of each gear 1, 3 A, 3 B, 2 to rotate and rotate. When the number is increased, a configuration that can effectively suppress the vibration and vibration of the gears 1, 3 A, 3 B, and 2 to ensure stable rotation is also employed. The anti-shake means 19a and 19b are shown only in the outer drive gear 1 and the first intermediate transmission gear 3A, but are also provided in the second intermediate transmission gear 3B and the inner main shaft gear 2 in the same manner.

又、図２において、２０は内側主軸ギヤ２の軸受ケースで、該内側主軸ギヤ２の主軸連結シャフト２１と一緒に回転するものであり、２２は後述する発電機、２３は固定支持金具２４に固定される保護枠、２５は発電機２２を構成する発電コイル支持金具で、ステンレスパイプ２６に固定されるものであり、上記固定支持金具２４はこの回転しないステンレスパイプ２６に取り付けられている。又、２７は化粧板で、該化粧板２７は上記した保持金具１７で抑えられている。   In FIG. 2, reference numeral 20 denotes a bearing case for the inner main shaft gear 2, which rotates together with the main shaft connecting shaft 21 of the inner main shaft gear 2, 22 is a generator which will be described later, and 23 is a fixed support bracket 24. A fixed protective frame 25 is a power generation coil support fitting constituting the generator 22, and is fixed to the stainless steel pipe 26. The fixed support fitting 24 is attached to the non-rotating stainless steel pipe 26. Reference numeral 27 denotes a decorative board, and the decorative board 27 is held by the holding metal 17 described above.

上記した発電機２２は、図５・図６に示す如く、内側主軸ギヤ２の主軸連結シャフト２１と一緒に回転する軸受ケース２０の外周面に複数の永久磁石２８を一定の間隔をおいて固定すると共に、上記発電コイル支持金具２５の内面に該各永久磁石２８と互いに向き合う複数のコイル巻線２９を固定する一方、各永久磁石２８を変形可能な板バネ３０を介して上記軸受ケース２０側に固定して、内側主軸ギヤ２の回転が停止している時は、各永久磁石２８が板バネ３０の力で軸受ケース２０側に引き寄せられて対応するコイル巻線２９との距離を拡げ、内側主軸ギヤ２が回転している時は、各永久磁石２８が板バネ３０の変形でコイル巻線２９側へ移動して対応するコイル巻線２９との距離を狭めるように構成されている。   As shown in FIGS. 5 and 6, the above-described generator 22 fixes a plurality of permanent magnets 28 at regular intervals on the outer peripheral surface of the bearing case 20 that rotates together with the main shaft coupling shaft 21 of the inner main shaft gear 2. At the same time, a plurality of coil windings 29 facing the permanent magnets 28 are fixed to the inner surface of the power generation coil support bracket 25, while the permanent magnets 28 are deformed through leaf springs 30 that can deform the bearing case 20 side. When the rotation of the inner main shaft gear 2 is stopped, each permanent magnet 28 is attracted to the bearing case 20 side by the force of the leaf spring 30 to increase the distance from the corresponding coil winding 29, When the inner main shaft gear 2 is rotating, each permanent magnet 28 is moved to the coil winding 29 side by deformation of the leaf spring 30 so that the distance from the corresponding coil winding 29 is reduced.

従って、この発電機２２の下で、内側主軸ギヤ２の回転が停止している時には、図７Ａに示す如く、上記した板バネ３０の直線形状から得られる弾力で、各永久磁石２８は、軸受ケース２０側に引き寄せられて、対応するコイル巻線２９との間隔Ｘを拡げるので、これにより、対応するコイル巻線２９との磁力圏内が解除されて、電力を発生しない。   Therefore, when the rotation of the inner main shaft gear 2 is stopped under the generator 22, as shown in FIG. 7A, each permanent magnet 28 is supported by the elastic force obtained from the linear shape of the leaf spring 30 described above. Since it is drawn to the case 20 side and the interval X with the corresponding coil winding 29 is widened, the magnetic field range with the corresponding coil winding 29 is thereby released, and no power is generated.

逆に、内側主軸ギヤ２が回転して回転数が上がると、今度は、図７Ｂに示す如く、各永久磁石２８に遠心力が働いて、当該各永久磁石２８が外側に引っ張られるので、これに伴い、板バネ３０が略台形形状に弾性変形して、各永久磁石２８を対応するコイル巻線２９側に自動的に移動させ、対応するコイル巻線２９との距離Ｙを狭めて、両者２８・２９を磁力圏内に入り込ませるので、これにより、電力を安定して発生させられる。   On the contrary, when the inner main shaft gear 2 rotates and the rotational speed increases, this time, as shown in FIG. 7B, centrifugal force is applied to each permanent magnet 28 and the permanent magnet 28 is pulled outward. Accordingly, the leaf spring 30 is elastically deformed into a substantially trapezoidal shape, and each permanent magnet 28 is automatically moved to the corresponding coil winding 29 side, and the distance Y from the corresponding coil winding 29 is reduced. Since 28 and 29 enter the magnetic field, power can be generated stably.

依って、上記した増速機を使用して斯かる発電機を稼働させる場合には、風力でブレードが回転するか水力で水車が回転すると、外側駆動ギヤ１が一緒に同方向に回転することとなるが、この外側駆動ギヤ１の回転は、第一ガイドローラー１３の押圧作用を得て、その内周咬合面４ａに形成された波形状の歯部５と第一中間伝達ギヤ３Ａの外周咬合面７ａに形成された波形状の歯部９ａとがその一部において咬合して回転力を伝達することとなる。この場合には、図８に示す如く、ガイドローラー１３の押圧方向において歯部５・９ａ同士が面接触状態をもって咬合を開始してから、数箇所での面接触状態をもって歯部５・９ａ同士の咬合が続き、その後、歯部５・９ａ同士の咬合が解かれることとなる。   Therefore, when such a generator is operated using the above-described speed increaser, the outer drive gear 1 rotates in the same direction together when the blade is rotated by wind power or the water turbine is rotated by hydraulic power. However, the rotation of the outer drive gear 1 obtains the pressing action of the first guide roller 13, and the wave-shaped tooth portion 5 formed on the inner peripheral occlusal surface 4a and the outer periphery of the first intermediate transmission gear 3A. The wavy tooth portion 9a formed on the occlusal surface 7a is engaged with a part thereof to transmit a rotational force. In this case, as shown in FIG. 8, the tooth portions 5 and 9 a start to engage with each other in the surface contact state in the pressing direction of the guide roller 13, and then the tooth portions 5 and 9 a have the surface contact state at several places. The occlusion of the tooth portions 5 and 9a is then released.

次いで、今度は、第一中間伝達ギヤ３Ａの内部において、第一中間伝達ギヤ３Ａの歯部９ｂと第二中間伝達ギヤ３Ｂの歯部１１ａとが咬合し、最後に、この第二中間伝達ギヤ３Ｂの歯部１１ｂと内側主軸ギヤ２の歯部１２とが咬合することとなるので、これにより、外側から内側へと回転力が伝達されて、回転スピードが増速されて行く。   Next, the tooth portion 9b of the first intermediate transmission gear 3A and the tooth portion 11a of the second intermediate transmission gear 3B are engaged with each other inside the first intermediate transmission gear 3A. Finally, the second intermediate transmission gear 3A is engaged. Since the tooth portion 11b of the 3B and the tooth portion 12 of the inner main shaft gear 2 are engaged with each other, the rotational force is transmitted from the outer side to the inner side, and the rotational speed is increased.

又、この外側から内側へ回転力が伝わる際には、径の大きなギヤ１から小さなギヤ３Ａ・３Ｂ・２と伝わりながら回転スピートが増していくので、中間伝達ギヤの数を増すと、夫々のギヤ比率が違うため、回転スピードが一層増速される。   Further, when the rotational force is transmitted from the outside to the inside, the rotational speed increases while being transmitted from the gear 1 having a large diameter to the gears 3A, 3B, and 2 having a small diameter. Therefore, when the number of intermediate transmission gears is increased, Since the gear ratio is different, the rotational speed is further increased.

しかも、各ギヤ１・３Ａ・３Ｂ・２の歯部５・９ａ・９ｂ・１１ａ・１１ｂ・１２は、緩やかな曲線の波形形状を呈しているので、各接触面積が多く且つ伝達面が数箇所と多くなるので、回転力を分散して伝えることができる。この為、外側駆動ギヤ１の回転力が少なくても、第一中間伝達ギヤ３Ａ・第二中間伝達ギヤ３Ｂを経て内側主軸ギヤ２に増速して伝えることが可能となる。又、回転しながら、外側から内側へと接触する際には、面から面に徐々に接触するため、騒音や振動を効果的に抑えることができる。特に、この場合には、上記した滑り止めリング１８が組み込まれているため、大きな効果を発揮する。   Moreover, since the tooth portions 5, 9a, 9b, 11a, 11b, and 12 of the gears 1, 3A, 3B, and 2 have a gently curved waveform shape, each contact area is large and the transmission surface is several places. Because it increases, the rotational force can be distributed and transmitted. For this reason, even if the rotational force of the outer drive gear 1 is small, it is possible to transmit it to the inner main shaft gear 2 through the first intermediate transmission gear 3A and the second intermediate transmission gear 3B. Further, when contacting from the outside to the inside while rotating, since the surface gradually contacts the surface, noise and vibration can be effectively suppressed. In particular, in this case, since the above-described anti-slip ring 18 is incorporated, a great effect is exhibited.

尚、上記実施例の下で、増速比を調べたところ、ブレードの回転数が３００ｒｐｍの時軸受ケース２０の回転数は６２４ｒｐｍ、ブレードの回転数が５００ｒｐｍの時軸受ケース２０の回転数は１０４０ｒｐｍであり、いずれも、約２．０８倍の増速比が得られた。   When the speed increase ratio was examined under the above embodiment, the rotation speed of the bearing case 20 was 624 rpm when the blade rotation speed was 300 rpm, and the rotation speed of the bearing case 20 was 1040 rpm when the blade rotation speed was 500 rpm. In either case, a speed increasing ratio of about 2.08 times was obtained.

従って、本実施例に係る増速機は、一般的なギヤに比べて接触面積が多いため、低速回転で高出力が発揮できるので、ブレードを小さくして、ビルの屋上や住宅街・商店街・駐車場などの色々な場所に設置しても、騒音・振動問題は生じないし、水力発電で使用する場合も、小さな川でも一定の流れがあれば、多くの電力を発電させることが可能となる。   Therefore, since the speed increaser according to the present embodiment has a larger contact area than a general gear, it can exhibit high output at low speed rotation. Therefore, the blade is made small, and the rooftop of a building, residential area / shopping street・ Noise and vibration problems do not occur even if installed in various places such as parking lots, and it is possible to generate a lot of power if it is used for hydropower generation or if there is a constant flow even in a small river. Become.

尚、上記した実施例は、発電機２２に使用される増速機を示したものであるが、本発明はこれに限定されるものではなく、本発明の精神に反しない限り、回転力を増速する必要があるものであれば、その他の電気自動車や送風機などにも使用することは十分に可能である。   In addition, although the above-mentioned Example showed the gearbox used for the generator 22, this invention is not limited to this, Unless it is contrary to the mind of this invention, rotational force is provided. If it is necessary to increase the speed, it can be sufficiently used for other electric vehicles and blowers.

本発明に係る増速機は、独特の波形状を呈するギヤを用いるだけで、低速回転で高出力を発揮できるので、これを回転力を増速する必要がある風力発電・水力発電、電気自動車、送風機などに応用すれば、頗る好都合なものとなる。   Since the speed increaser according to the present invention can exhibit high output at low speed rotation only by using a gear having a unique wave shape, it is necessary to increase the rotational force of the wind power generation / hydroelectric power generation, electric vehicle. If applied to a blower or the like, it will be more convenient.

１ 外側駆動ギヤ
２ 内側伝達ギヤ
３Ａ 第一中間伝達ギヤ
３Ｂ 第二中間伝達ギヤ
４ａ 外側駆動ギヤの内周咬合面
４ｂ 外側駆動ギヤの内周非咬合面
５ 外側駆動ギヤの内周歯部
６ 外側駆動ギヤの内周案内溝
７ａ 第一中間伝達ギヤの外周咬合面
７ｂ 第一中間伝達ギヤの外周非咬合面
８ａ 第一中間伝達ギヤの内周咬合面
８ｂ 第一中間伝達ギヤの内周非咬合面
９ａ 第一中間伝達ギヤの外周歯部
９ｂ 第一中間伝達ギヤの内周歯部
１０ａ 第一中間伝達ギャの外周案内溝
１０ｂ 第一中間伝達ギヤの内周案内溝
１１ａ 第二中間伝達ギヤの外周歯部
１１ｂ 第二中間伝達ギヤの内周歯部
１２ 内側主軸ギヤの外周歯部
１３ 第一ガイドローラー
１４ 第二ガイドローラー
１５ 第三ガイドローラー
１６ 連結腕
１７ 保持金具
１８ 滑り止めリング
１９ａ ブレ防止手段
１９ｂ ブレ防止手段
２０ 内側主軸ギヤの軸受ケース
２１ 主軸連結シャフト
２２ 発電機
２３ 保護枠
２４ 固定支持金具
２５ 発電コイル支持金具
２６ 連結主軸
２７ 保護板
２８ 永久磁石
２９ コイル巻線
３０ 板バネ
Ｘ 停止時の永久磁石とコイル巻線との距離
Ｙ 起動時の永久磁石とコイル巻線との距離 DESCRIPTION OF SYMBOLS 1 Outer drive gear 2 Inner transmission gear 3A 1st intermediate transmission gear 3B 2nd intermediate transmission gear 4a Inner peripheral occlusal surface 4b of outer drive gear 5 Inner peripheral non-occlusion surface of outer drive gear 5 Outer peripheral tooth portion 6 Outer drive gear Inner peripheral guide groove 7a of the first intermediate transmission gear 7b Outer peripheral occlusal surface of the first intermediate transmission gear 8a Inner peripheral occlusal surface of the first intermediate transmission gear 8b Inner peripheral non-engagement of the first intermediate transmission gear Surface 9a Outer peripheral tooth portion of the first intermediate transmission gear 9b Inner peripheral tooth portion of the first intermediate transmission gear 10a Outer peripheral guide groove of the first intermediate transmission gear 10b Inner peripheral guide groove of the first intermediate transmission gear 11a of the second intermediate transmission gear Outer peripheral tooth portion 11b Inner peripheral tooth portion of second intermediate transmission gear 12 Outer peripheral tooth portion of inner main shaft gear 13 First guide roller 14 Second guide roller 15 Third guide roller 16 Connecting arm 17 Holding bracket 18 Non-slip ring 9a Shake prevention means 19b Shake prevention means 20 Inner main shaft gear bearing case 21 Main shaft connecting shaft 22 Generator 23 Protective frame 24 Fixed support fitting 25 Power generation coil support fitting 26 Connecting main shaft 27 Protection plate 28 Permanent magnet 29 Coil winding 30 Plate spring X Distance between permanent magnet and coil winding at stop Y Distance between permanent magnet and coil winding at startup

Claims (4)

エネルギーを受けて回転する外側駆動ギヤと、該外側駆動ギヤの回転力を回転体に伝える内側主軸ギヤとを備え、上記外側駆動ギヤと内側主軸ギヤとの間に複数の中間伝達ギヤを咬合可能に配設し、外側駆動ギヤの回転力を上記各中間伝達ギヤと内側主軸ギヤとで増速して、上記回転体を該増速された回転出力で回転させる増速機であって、上記各ギヤは、径の異なるリング状に成形されて、各ギヤの対向する内・外周面に咬合面と非咬合面とを有し、各ギヤごとで対向する咬合面に波形状を呈する歯部を連続して形成し、該対向する各波形状の歯部の面接触による咬合状態を得て、外側駆動ギヤの回転力を各波形状の歯部を介して内側主軸ギヤに伝達すると共に、各ギヤの上記対向する非咬合面間にガイドローラーを介設して、該ガイドローラーの押圧方向において対向する波形状の歯部同士を咬合させることを特徴とする増速機。   An outer drive gear that rotates by receiving energy and an inner main shaft gear that transmits the rotational force of the outer drive gear to the rotating body, and a plurality of intermediate transmission gears can be engaged between the outer drive gear and the inner main shaft gear. A speed increasing device for increasing the rotational force of the outer drive gear with the intermediate transmission gear and the inner main shaft gear, and rotating the rotating body with the increased rotational output. Each gear is formed in a ring shape having a different diameter, and has an occlusal surface and a non-occlusal surface on the inner and outer peripheral surfaces opposed to each gear, and a tooth portion having a wave shape on the opposed occlusal surface for each gear. Are continuously formed to obtain an occlusal state due to surface contact between the respective wave-shaped tooth portions facing each other, and the rotational force of the outer drive gear is transmitted to the inner main shaft gear via the wave-shaped tooth portions. A guide roller is interposed between the opposing non-occlusion surfaces of each gear, and the guide roller Up gear, characterized in that to bite the corrugated toothing facing each other in the pressing direction of the error. 各ギヤの対向する咬合面間に波形状の歯部と相似する滑り止めリングを組み込んだことを特徴とする請求項１記載の増速機。   The speed increasing gear according to claim 1, wherein a non-slip ring similar to a wave-shaped tooth portion is incorporated between the occlusal surfaces facing each gear. 各ギヤの非咬合面間に介設されるガイドローラーは、内・外の各段ごとで、介設位置が交互に逆向きとなっていることを特徴とする請求項１乃至請求項２のいずれかに記載の増速機。   3. The guide roller interposed between the non-occlusion surfaces of each gear has an interposed position alternately opposite in each of the inner and outer steps. A speed increaser according to any one of the above. 各ギヤの咬合面と非咬合面の境にギヤのブレ防止手段を設けたことを特徴とする請求項１乃至請求項３記載の増速機。   4. The speed increaser according to claim 1, further comprising a gear anti-shake means provided at a boundary between the occlusal surface and the non-occlusal surface of each gear.
JP2010183202A 2010-08-18 2010-08-18 Speed increaser Expired - Fee Related JP5167318B2 (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016006519A1 (en) * 2014-07-07 2016-01-14 圀博 三宅 Hybrid vehicle
JP2017122431A (en) * 2016-01-05 2017-07-13 三森株式会社 Dual-shell type fluid power generation device and rotor module thereof
DE102016116438B3 (en) * 2016-09-02 2018-01-18 Witzenmann Gmbh Output element for a stress wave transmission

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Publication number Priority date Publication date Assignee Title
JPS4936897B1 (en) * 1968-10-12 1974-10-04
JPS5227956A (en) * 1975-08-28 1977-03-02 Kazuo Okuno Rotary device for trnsmitting rotation
JPS5327761A (en) * 1976-08-25 1978-03-15 Shiyuuji Hirai Power conversion and transmission mechanism
JPH0343149U (en) * 1989-09-06 1991-04-23
JP2006522294A (en) * 2003-04-04 2006-09-28 ハンマーベック，ジョン，ピー．，アール． Ratio conversion method and apparatus
JP2007309430A (en) * 2006-05-18 2007-11-29 Denso Corp Reduction gear and valve timing adjusting device

Patent Citations (6)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS4936897B1 (en) * 1968-10-12 1974-10-04
JPS5227956A (en) * 1975-08-28 1977-03-02 Kazuo Okuno Rotary device for trnsmitting rotation
JPS5327761A (en) * 1976-08-25 1978-03-15 Shiyuuji Hirai Power conversion and transmission mechanism
JPH0343149U (en) * 1989-09-06 1991-04-23
JP2006522294A (en) * 2003-04-04 2006-09-28 ハンマーベック，ジョン，ピー．，アール． Ratio conversion method and apparatus
JP2007309430A (en) * 2006-05-18 2007-11-29 Denso Corp Reduction gear and valve timing adjusting device

Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
WO2016006519A1 (en) * 2014-07-07 2016-01-14 圀博 三宅 Hybrid vehicle
JP2017122431A (en) * 2016-01-05 2017-07-13 三森株式会社 Dual-shell type fluid power generation device and rotor module thereof
DE102016116438B3 (en) * 2016-09-02 2018-01-18 Witzenmann Gmbh Output element for a stress wave transmission

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