JP2019070375A - Power generator - Google Patents

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JP2019070375A
JP2019070375A JP2017197867A JP2017197867A JP2019070375A JP 2019070375 A JP2019070375 A JP 2019070375A JP 2017197867 A JP2017197867 A JP 2017197867A JP 2017197867 A JP2017197867 A JP 2017197867A JP 2019070375 A JP2019070375 A JP 2019070375A
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wind
rotating body
gear
power
power gear
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JP6391129B1 (en
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佳仁 佐藤
Yoshihito Sato
佳仁 佐藤
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HOUSEPLAN CO Ltd
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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
    • Y02E10/20—Hydro energy
    • 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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  • Hydraulic Turbines (AREA)
  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)

Abstract

To provide a power generator which can obtain sufficient rotation torque and effectively utilize fluid force even if the fluid force is weak.SOLUTION: A power generator includes: a main rotary shaft 3; a first rotating body 21a which rotates around the main rotary shaft 3 in a first direction by fluid force; a second rotating body 21b which has a second rotary surface facing in parallel to a first rotary surface defined by the first rotating body and in which the second rotary surface rotates around the main rotary shaft 3 in a second direction opposite to the first direction by the fluid force; a first power gear 31a which receives rotation torque by the first rotating body 21a and the second rotating body 21b to rotate; and a first power generator 62a which is driven by rotation of the first power gear 31a.SELECTED DRAWING: Figure 2

Description

本発明は、流体力による回転力を利用した発電装置に関する。   TECHNICAL FIELD The present invention relates to a power generation device utilizing a rotational force by a fluid force.

発電には、風力や水力などの流体力による回転力を利用したものがある。「流体力」とは、空気や水等の流体の流れによって引き起こされる力のことである。流れてくる風や水等の流体を発電装置が直接的に受け、受けた力を回転力に変え、発電用のタービンを回転させることができる。風を利用した風力発電、河川などの流水を利用した水力発電、潮汐運動を利用した潮汐発電、海流を利用した潮流発電など、自然エネルギーの流体力を取り入れた発電方法が各種開発されている。   There are power generation devices that use the rotational force of fluid such as wind power and water power. "Fluid force" is the force caused by the flow of fluid such as air or water. It is possible to directly receive a fluid such as wind or water flowing from the generator, convert the received force into a rotational force, and rotate a turbine for power generation. Various power generation methods have been developed that take in the fluid power of natural energy, such as wind power generation using wind, hydropower generation using flowing water such as rivers, tidal power generation using tidal motion, and tidal power generation using ocean current.

自然エネルギーはクリーンであり、無償で得られるという利点があるが、エネルギー量も自然任せとなりがちであり、発電量が不安定になりやすい。風力発電を例にとると、発電量は利用可能な風力に依存する。定点当たりの風速を一定とすると、取り込める風量が多いほど発電量は大きくなる。風は、常に一定の風速で吹くわけではない。十分に風況観測を行い、しかるべき土地に風力発電装置を設置しても、日により時間帯により風速は安定せず、発電量も不安定となりやすいという欠点がある。風速が大きすぎる場合は、風力発電装置に負荷がかかり危険なため、発電機の回転を止めて空転をさせる必要がある。一方で風速が小さすぎると、発電を開始する程度の回転力を得られない。特に内陸部など風向が定まりにくいところでは、風速も小さくなる傾向があるため、低速時の発電の効率化が問題となる。   Natural energy has the advantage of being clean and obtained free of charge, but the amount of energy tends to be left to nature, and the amount of power generation tends to be unstable. Taking wind power as an example, the amount of power generation depends on the available wind power. Assuming that the wind speed per fixed point is constant, the amount of power generation increases as the amount of wind that can be taken in increases. Wind does not always blow at a constant wind speed. Even if wind conditions are sufficiently observed and wind power generators are installed on appropriate lands, the wind speed is not stable depending on the time of day, and the amount of power generation tends to be unstable. If the wind speed is too high, it is necessary to stop the rotation of the generator and cause it to idle because the wind power generator is loaded and dangerous. On the other hand, if the wind speed is too low, the rotational power to start power generation can not be obtained. In particular, where the wind direction is difficult to determine, such as in the inland, the wind speed also tends to be low, so the problem is how to make efficient power generation at low speeds.

Ｎを単線密巻コイルの巻数、ΔΦ／Δtを微小時間Δtでのコイルを貫く磁束の変化とすると、ファラデーの電磁誘導の法則から、単線密巻コイルの誘導起電力Ｖは：

Ｖ＝−ＮΔΦ/Δt …………（１）

と表わされる。即ち、発電機の開放電圧は、磁束の変化、即ち発電機の回転数に依存する。特許文献１には、低速回転では極数が多い方が有利であり、高速回転では極数が少ない方が有利であることが記載されている。特許文献１には更に、低速回転では極数が多い方が有利であるが、極数が多くなると内部抵抗が増え、大きな回転トルクが必要になることも示されている。よって、発電機として広く普及している多極発電機を用いる際、低速回転せざるを得ないような風力下にて発電量を多くするには、回転トルクを大きくする工夫をしなければならない。 Assuming that N is the number of turns of a single wire closely wound coil, and Δ 変 化 / Δt is a change in magnetic flux passing through the coil at a minute time Δt, the induced electromotive force V of the single wire closely wound coil is:

V = −NΔΦ / Δt ...... (1)

It is expressed as That is, the open circuit voltage of the generator depends on the change of the magnetic flux, i.e. the number of revolutions of the generator. Patent Document 1 describes that it is advantageous that the number of poles is large in low speed rotation, and that it is advantageous that the number of poles is small in high speed rotation. Patent Document 1 further shows that although it is advantageous that the number of poles is large at low speed rotation, the internal resistance increases as the number of poles increases and a large rotational torque is required. Therefore, when using a multipolar generator widely used as a generator, in order to increase the amount of power generation under wind power where it is necessary to rotate at low speed, it is necessary to devise a large rotational torque .

特許文献２及び３では、風車の風受け羽根の形状を風向により可変にすることで、一方の風受け羽根が風を受けて開くと、風の向きに対抗する他方の風受け羽根が閉じて風の抵抗を小さくするため、全体として発電に利用できる風力エネルギーを多く取り込める構造となっている。しかし、このような従来技術では、風受け羽根が風に対抗する向きになるときに風の抵抗を受けにくいような動的構造に設計されているにとどまり、回転トルクを大きくするための工夫としては不十分であった。   In the patent documents 2 and 3, when one wind receiving blade receives a wind and opens by making the shape of the wind receiving blade of a windmill variable by wind direction, the other wind receiving blade which opposes the direction of wind closes. In order to reduce wind resistance, it has a structure that can capture a large amount of wind energy that can be used for power generation as a whole. However, in such a prior art, the wind receiving blade is designed to have a dynamic structure that is less susceptible to wind resistance when facing the wind, and as a device for increasing the rotational torque. Was inadequate.

以上、風力発電を例にとって説明したが、同じく自然の流体の流体力を利用する水力発電や潮汐発電などにおいても、自然の流体力の動態が不安定である故に、同様の問題が生じやすい傾向がある。   As described above, wind power generation has been described as an example, but also in hydroelectric power generation and tidal power generation that use the fluid power of natural fluid, the same problem is likely to occur because the dynamics of the natural power is unstable. There is.

特許第５３８３９９０号公報Patent No. 5383990 gazette 特許第５８５０１２４号公報Patent No. 5850124 特許第５３６８５３９号公報Patent No. 5368539 gazette

本発明は上記の問題に着目してなされたものであって、流体力の弱い場合であっても十分な回転トルクが得られ、流体力を有効に利用できる発電装置を提供することを目的とする。   The present invention has been made in view of the above problems, and it is an object of the present invention to provide a power generation apparatus capable of obtaining sufficient rotational torque even when the fluid force is weak and effectively utilizing the fluid force. Do.

上記目的を達成するために、本発明の態様は、（ａ）主回転軸と、（ｂ）流体力により主回転軸の周りを第１方向に回転する第１の回転体と、（ｃ）この第１の回転体が定義する第１の回転面と平行に対向する第２の回転面を有し、この第２の回転面が第１方向と反対の第２方向に、流体力により主回転軸の周りを回転する第２の回転体と、（ｄ）これらの第１及び第２の回転体の両者によって回転トルクが付与されて回転する第１の動力ギアと、（ｅ）この第１の動力ギアの回転によって駆動される第１の発電機を備える発電装置であることを要旨とする。   In order to achieve the above object, an aspect of the present invention comprises: (a) a main rotating shaft; (b) a first rotating body that rotates in a first direction around the main rotating shaft by a fluid force; The first rotating body has a second rotation surface facing in parallel to a first rotation surface defined by the first rotation body, and the second rotation surface is mainly driven by a fluid force in a second direction opposite to the first direction. A second rotating body that rotates around the rotation axis; (d) a first power gear that is rotated by applying rotational torque by both of the first and second rotating bodies; (e) the second rotating body A gist of the present invention is a power generation device including a first generator driven by rotation of one power gear.

本発明によれば、流体力の弱い場合であっても十分な回転トルクが得られ、流体力を有効に利用できる発電装置を提供することができる。   According to the present invention, a sufficient power generation torque can be obtained even when the fluid force is weak, and it is possible to provide a power generator capable of effectively utilizing the fluid force.

本発明の第１の実施の形態に係る発電装置の斜視図である。FIG. 1 is a perspective view of a power generation device according to a first embodiment of the present invention. 本発明の第１の実施の形態に係る発電装置の正面図である。It is a front view of the electric power generating apparatus which concerns on the 1st Embodiment of this invention. 図２のＡ部分の拡大図である。It is an enlarged view of A part of FIG. 図３のＡ−Ａ方向から見た拡大断面図である。It is an expanded sectional view seen from the AA direction of FIG. 本発明の第１の実施の形態に係る発電装置の上面図である。It is a top view of the electric power generating apparatus which concerns on the 1st Embodiment of this invention. 図６（ａ）は平歯車形状の第１の動力ギアの斜視図であり、図６（ｂ）は図６（ａ）の上面図である。6 (a) is a perspective view of a spur gear-shaped first power gear, and FIG. 6 (b) is a top view of FIG. 6 (a). 図６（ａ）の第１の動力ギアの歯にかみ合う第１の駆動ギアの歯を有する第１の輪状フレームの斜視図である。FIG. 7 is a perspective view of a first annular frame with teeth of a first drive gear meshing with the teeth of the first power gear of FIG. 6 (a). 図８（ａ）は、すぐばかさ歯車形状の第１の動力ギアの斜視図であり、図８（ｂ）は図８（ａ）の上面図である。FIG. 8 (a) is a perspective view of a straight bevel gear shaped first power gear, and FIG. 8 (b) is a top view of FIG. 8 (a). 図８（ａ）の第１の動力ギアの歯にかみ合う第１の駆動ギアの歯を有する第１の輪状フレームの斜視図である。FIG. 9 is a perspective view of a first annular frame with teeth of a first drive gear meshing with the teeth of the first power gear of FIG. 8 (a); 本発明の第１の実施の形態に係る発電装置に図８（ａ）の第１の動力ギアを使用した場合の、図３相当の図である。It is a figure equivalent to FIG. 3 at the time of using the 1st power gear of FIG. 8 (a) for the electric power generating apparatus which concerns on the 1st Embodiment of this invention. 図８（ａ）の第１の動力ギアと図９の第１の輪状フレームの使用状態の部分斜視図である。FIG. 10 is a partial perspective view of the first power gear of FIG. 8 (a) and the first annular frame of FIG. 9 in use; 本発明の第１の実施の形態の変形例に係る発電装置の正面図である。It is a front view of the electric power generating apparatus which concerns on the modification of the 1st Embodiment of this invention. 本発明の第２の実施の形態に係る発電装置の斜視図１である。It is the perspective view 1 of the electric power generating apparatus which concerns on the 2nd Embodiment of this invention. 本発明の第２の実施の形態に係る発電装置の正面図である。It is a front view of the electric power generating apparatus which concerns on the 2nd Embodiment of this invention. 図１４のＡ部分の拡大図である。It is an enlarged view of A part of FIG. 図１５のＡ−Ａ方向から見た拡大断面図である。It is the expanded sectional view seen from the AA direction of FIG. 本発明の第２の実施の形態に係る発電装置の斜視図２である。It is a perspective view 2 of the electric power generating apparatus which concerns on the 2nd Embodiment of this invention. 本発明の第３の実施の形態に係る発電装置の正面図である。It is a front view of the electric power generating apparatus which concerns on the 3rd Embodiment of this invention. 図１８のＡ部分の拡大図である。It is an enlarged view of A part of FIG. 図１９のＡ−Ａ方向から見た拡大断面図である。It is the expanded sectional view seen from the AA direction of FIG. 本発明の第３の実施の形態に係る発電装置の第１の駆動ギアを有する第１の輪状フレームの上面図である。It is a top view of the 1st ring-shaped frame which has the 1st drive gear of the electric power generating apparatus which concerns on the 3rd Embodiment of this invention. 本発明の第４の実施の形態に係る発電装置の正面図である。It is a front view of the electric power generating apparatus which concerns on the 4th Embodiment of this invention. 本発明の第５の実施の形態に係る発電装置の斜視図である。It is a perspective view of the electric power generating apparatus which concerns on the 5th Embodiment of this invention. 図２３のＣ部分の拡大正面図である。It is an enlarged front view of C part of FIG. 図２４のＡ−Ａ方向から見た拡大断面図である。It is the expanded sectional view seen from the AA direction of FIG. 本発明の第５の実施の形態の変形例に係る発電装置の斜視図である。It is a perspective view of the electric power generating apparatus which concerns on the modification of the 5th Embodiment of this invention. 他の実施の形態に係る発電装置の斜視図である。It is a perspective view of the electric power generating apparatus which concerns on other embodiment. 図２７のＣ部分の拡大正面図である。It is an enlarged front view of C part of FIG. 図２８のＡ−Ａ方向から見た拡大断面図である。It is the expanded sectional view seen from the AA direction of FIG. 図３０（ａ）は、お椀型の風受け羽根の形状の正面図、図３０（ｂ）は図３０（ａ）の側面図、図３０（ｃ）は図３０（ａ）の背面図、図３０（ｄ）は図３０（ａ）の斜視図である。FIG. 30 (a) is a front view of the shape of a bowl-shaped wind receiving blade, FIG. 30 (b) is a side view of FIG. 30 (a), and FIG. 30 (c) is a rear view of FIG. 30 (d) is a perspective view of FIG. 30 (a). 図３１（ａ）はお椀型の変形タイプの風受け羽根の形状の正面図、図３１（ｂ）は図３１（ａ）の側面図、図３１（ｃ）は図３１（ａ）の背面図、図３１（ｄ）は図３１（ａ）の斜視図である。31 (a) is a front view of the shape of a bowl-shaped deformation type wind receiving blade, FIG. 31 (b) is a side view of FIG. 31 (a), and FIG. 31 (c) is a rear view of FIG. 31 (a) 31 (d) is a perspective view of FIG. 31 (a).

以下において、図面を参照して、本発明の第１〜第５の実施の形態を説明し、流体力の弱い場合であっても十分な回転トルクが得られ、流体力を有効に利用できる発電装置の構造を説明する。以下の図面の記載において、同一又は類似の部分には同一又は類似の符号を付している。ただし、図面は模式的なものであり、厚みと平面寸法との関係、各部材の大きさの比率等は現実のものとは異なることに留意すべきである。例えば、第１及び第２の駆動ギアに対する第１の動力ギアとのギア比や直径の比等は例示に過ぎず、以下の説明の内容に狭く限定されるものではない。したがって、具体的な厚み、寸法、ギア比等は以下の説明から理解できる技術的思想の趣旨を参酌してより多様に判断すべきものである。又、図面相互間においても互いの寸法の関係や比率が異なる部分が含まれていることは勿論である。   In the following, first to fifth embodiments of the present invention will be described with reference to the drawings, and a sufficient rotational torque can be obtained even when the fluid force is weak, and a power generation capable of effectively utilizing the fluid force The structure of the device will be described. In the following description of the drawings, the same or similar parts are denoted by the same or similar reference numerals. However, it should be noted that the drawings are schematic, and the relationship between the thickness and the planar dimension, the ratio of the size of each member, and the like are different from actual ones. For example, the gear ratio and the diameter ratio of the first power gear to the first and second drive gears are merely examples, and the present invention is not narrowly limited to the contents of the following description. Therefore, specific thicknesses, dimensions, gear ratios, etc. should be judged in various ways in consideration of the spirit of the technical idea that can be understood from the following description. Moreover, it is needless to say that parts having different dimensional relationships and proportions are included among the drawings.

又、以下に示す第１〜第５の実施の形態は、本発明の技術的思想を具体化するための装置を例示するものであって、本発明の技術的思想は、構成部品の材質、形状、構造、配置等を下記のものに特定するものではない。特に以下の説明では、流体力として風力を取り上げ、発電装置として風力発電装置について説明するが、本発明はそれに限ったものではなく、水力発電装置や潮汐発電装置などへ応用することができる。また以下の説明においては、風力発電装置の中でも垂直軸を有するパドル型風車を例示して主に説明するが、本発明はそれに限ったものではない。２以上の回転体を有するならば、他の垂直軸型風車、例えばジャイロミル型やサボニウス型、Ｓ字型等の風車へも本発明は適用可能である。又、プロペラ型風車等の水平軸型の風車へも、主回転軸の方向の変更をすることで、本発明は適用可能な技術的概念である。このように、本発明の技術的思想は、第１〜第５の実施の形態で記載された内容に限定されず、特許請求の範囲に記載された請求項が規定する技術的範囲内において、種々の変更を加えることができる。   In addition, the first to fifth embodiments described below illustrate apparatuses for embodying the technical idea of the present invention, and the technical idea of the present invention includes materials of components, The shape, structure, arrangement, etc. are not specified in the following. In particular, in the following description, wind power is taken as the fluid force, and a wind power generator is described as a power generation device. However, the present invention is not limited thereto, and can be applied to a hydro power generator or a tidal power generator. Further, in the following description, among the wind power generators, a paddle type wind turbine having a vertical axis is mainly illustrated and described, but the present invention is not limited thereto. The present invention is also applicable to other vertical axis wind turbines, such as a gyro mill type, a Savonius type, and an S-shaped wind turbine, as long as they have two or more rotating bodies. Further, the present invention is a technical concept applicable to a horizontal axis type wind turbine such as a propeller type wind turbine by changing the direction of the main rotation axis. Thus, the technical idea of the present invention is not limited to the contents described in the first to fifth embodiments, but within the technical scope defined by the claims described in the claims. Various changes can be made.

（第１の実施の形態）
図１及び図２に示すように、本発明の第１の実施の形態に係る発電装置は、主回転軸３と、流体力（風力）により主回転軸３の周りを第１方向（図１のＣ方向）に回転する第１の回転体２１ａと、第１の回転体が定義する第１の回転面と平行に対向する第２の回転面を有し、第２の回転面が第１方向と反対の第２方向（図１のＢ方向）に、流体力（風力）により主回転軸３の周りを回転する第２の回転体２１ｂを備える。第１の実施の形態に係る発電装置は更に、第１の回転体２１ａ及び第２の回転体２１ｂの両者によって回転トルクが付与されて回転する第１の動力ギア３１ａと、第１の動力ギア３１ａの回転によって駆動される第１の発電機６２ａを備える。 First Embodiment
As shown in FIGS. 1 and 2, the power generation apparatus according to the first embodiment of the present invention has a main rotating shaft 3 and a first direction (FIG. 1) around the main rotating shaft 3 by fluid force (wind force). Of the first rotation body 21a rotating in the direction C) and a second rotation surface facing in parallel with the first rotation surface defined by the first rotation body, the second rotation surface being the first In a second direction (direction B in FIG. 1) opposite to the direction, a second rotating body 21b is provided which rotates around the main rotation axis 3 by fluid force (wind force). The power generation apparatus according to the first embodiment further includes a first power gear 31a that is rotated by applying a rotational torque by both the first rotating body 21a and the second rotating body 21b, and a first power gear 31a. A first generator 62a driven by the rotation of 31a is provided.

第１の実施の形態に係る発電装置における「第１の回転面」は、図１に示された主回転軸３が鉛直方向の態様では、以下のとおり定義される。第１の回転体２１ａを構成する部材うち、最も上部に位置する最上部部材の最上部点の円軌道が描く面を「最上面」、最も下部に位置する最下部部材の最下部点の円軌道が描く面を「最下面」とする。そして、この第１の回転体２１ａの最上面が延長される面と第１の回転体２１ａの最下面が延長される面に挟まれる空間において、第１の回転体２１ａの最も主回転軸から遠い部材の最外周側の一点を「第１の回転体２１ａの外周点」と定義する。第１の回転体２１ａの外周点が一点に定まらない場合、たとえば、最も主回転軸から遠い部材の最外周側が点でなく面である場合は、その面上の任意の一点を選択し、「第１の回転体２１ａの外周点」とする。つまり、回転体の最外周側の任意の一点が「第１の回転体２１ａの外周点」となるので、「第１の回転体２１ａの外周点」は最上面が延長される面と最下面が延長される面に挟まれる空間において、無限に存在する。   The “first rotation surface” in the power generation device according to the first embodiment is defined as follows in the aspect in which the main rotation shaft 3 shown in FIG. 1 is in the vertical direction. Among the members constituting the first rotary body 21a, the surface drawn by the circular orbit of the topmost point of the topmost member located at the top is the "top face", and the circle of the bottommost point of the bottommost member located at the bottom The surface drawn by the orbit is the "bottom surface". Then, in the space between the surface to which the uppermost surface of the first rotary body 21a is extended and the surface to which the lowermost surface of the first rotary body 21a is extended, from the main rotation axis of the first rotary member 21a One point on the outermost side of the distant member is defined as "the outer peripheral point of the first rotating body 21a". If the outer peripheral point of the first rotating body 21a is not fixed to one point, for example, if the outermost peripheral side of the member farthest from the main rotation axis is not a point but a surface, select any one point on that surface. The outer circumferential point of the first rotating body 21 a is taken as That is, since any one point on the outermost side of the rotating body is the “outer peripheral point of the first rotating body 21 a”, “the outer peripheral point of the first rotating body 21 a” is the surface and the lowermost surface where the uppermost surface is extended Exists infinitely in the space between the faces to be extended.

即ち、第１の回転体２１ａの最上面が延長される面と第１の回転体２１ａの最下面が延長される面に挟まれる空間において、第１の回転体２１ａを主回転軸の周りに一回転させた際の任意の外周点が描く軌跡を「第１の回転体２１ａの外周円」としたとき、その第１の回転体２１ａの外周円で囲まれた円盤を「第１の回転面」と定義する。よって、「第１の回転面」は、第１の回転体２１ａの最上面が延長される面と第１の回転体２１ａの最下面が延長される面に挟まれる空間において、平行な円盤として無数に存在することが可能である。   That is, in the space between the surface to which the uppermost surface of the first rotary body 21a is extended and the surface to which the lowermost surface of the first rotary body 21a is extended, the first rotary body 21a is arranged around the main rotation axis. Assuming that the locus drawn by an arbitrary outer peripheral point when making one rotation is "the outer peripheral circle of the first rotating body 21a", the disk surrounded by the outer peripheral circle of the first rotating body 21a is "the first rotation It is defined as "face". Therefore, the “first rotation surface” is a parallel disk in a space sandwiched by the surface to which the top surface of the first rotation body 21a is extended and the surface to which the bottom surface of the first rotation body 21a is extended. It is possible to exist innumerably.

図１に示された主回転軸３が鉛直方向の態様を用いて「第２の回転面」も同様に定義される。即ち、第２の回転体２１ｂの最上面が延長される面と第２の回転体２１ｂの最下面が延長される面に挟まれる空間において、第２の回転体２１ｂを主回転軸の周りに一回転させた際の第２の回転体２１ｂの任意の外周点が描く軌跡を「第２の回転体２１ｂの外周円」としたとき、その第２の回転体２１ｂの外周円で囲まれた円盤を「第２の回転面」と定義する。よって、「第２の回転面」も、第２の回転体２１ｂの最上面が延長される面と第２の回転体２１ｂの最下面が延長される面に挟まれる空間において、平行な円盤として無数に存在することが可能である。   The “second plane of rotation” is defined in the same manner, using the aspect that the main rotation axis 3 shown in FIG. 1 is in the vertical direction. That is, in the space between the surface to which the uppermost surface of the second rotary body 21b is extended and the surface to which the lowermost surface of the second rotary body 21b is extended, the second rotary body 21b is arranged around the main rotation axis. When the locus drawn by an arbitrary outer peripheral point of the second rotating body 21b when making one rotation is "the outer peripheral circle of the second rotating body 21b", it is surrounded by the outer peripheral circle of the second rotating body 21b. The disk is defined as "the second surface of rotation". Therefore, the “second rotation surface” is also a parallel disk in a space sandwiched by the surface to which the top surface of the second rotation body 21b is extended and the surface to which the bottom surface of the second rotation body 21b is extended. It is possible to exist innumerably.

なお、図１に示された態様は例示であり、以下の第１〜第５の実施の形態の説明における「左右」や「上下」の方向は、単に説明の便宜上の定義であって、本発明の技術的思想を限定するものではない。よって、主回転軸３が水平方向であれば、紙面を９０度回転すれば「左右」と「上下」とは交換して読むことになり、「第１の回転面」「第２の回転面」の定義も読み替える必要があることは勿論である。   In addition, the aspect shown by FIG. 1 is an illustration, and the direction of "left and right" and "upper and lower" in the description of the following 1st-5th embodiment is only the definition for convenience of explanation, It does not limit the technical idea of the invention. Therefore, if the main rotary shaft 3 is in the horizontal direction, "left and right" and "upper and lower" will be exchanged and read if the paper surface is rotated 90 degrees, and "first rotary surface" "second rotary surface" Of course, the definition of "" also needs to be read.

第１の実施の形態に係る発電装置は、風向がほぼ限られている場所であれば、重力方向に主回転軸３を置く垂直軸型ではなく、水平方向に主回転軸を置く水平軸型の風車へ応用することもできる。水平軸型の風車には、風向を検知して風に正対するよう調整する機構のあるプロペラ型風車等が適しているが、風向がほぼ限られているような地域では、水平軸を持つパドル型風車等も利用可能である。いずれにせよ、図１の斜視図に例示したように、第１の実施の形態に係る発電装置においては、主回転軸３は土台１に据え付けられ、重力方向に直立し、第２方向（Ｂ方向と同一となるＡ方向）に回転する場合について説明する。土台１の内部には、主回転軸３の回転エネルギーを取り出すための発電機が設置されていてもよい。   The power generation apparatus according to the first embodiment is not a vertical axis type in which the main rotation axis 3 is set in the gravity direction but a horizontal axis type in which the main rotation axis is set in the horizontal direction. It can also be applied to wind turbines. A propeller-type wind turbine with a mechanism that detects the wind direction and adjusts it to face the wind is suitable for horizontal-axis wind turbines, but in areas where the wind direction is almost limited, paddles with horizontal axes are suitable. Wind turbines and the like can also be used. In any case, as illustrated in the perspective view of FIG. 1, in the power generation apparatus according to the first embodiment, the main rotation shaft 3 is installed on the base 1 and stands upright in the direction of gravity, and the second direction (B The case of rotating in the direction A) which is the same as the direction will be described. A generator for extracting rotational energy of the main rotation shaft 3 may be installed inside the base 1.

図１及び図２に示すように、第１の実施の形態に係る発電装置の第１の回転体２１ａは第１の輪状フレーム８１ａを備え、第２の回転体２１ｂは第２の輪状フレーム８１ｂを備える。即ち、第１の回転体２１ａは、第１の回転体２１ａの最上面が延長される面と第１の回転体２１ａの最下面が延長される面に挟まれる空間において、任意に選択された第１の回転面の一部を構成する第１の輪状フレーム８１ａを第１の回転体２１ａの外周側に有する。同様に、第２の回転体２１ｂは、第２の回転体２１ｂの最上面が延長される面と第２の回転体２１ｂの最下面が延長される面に挟まれる空間において、任意に選択された第２の回転面の一部を構成する第２の輪状フレーム８１ｂを第２の回転体２１ｂの外周側に有する。第１の輪状フレーム８１ａの直径方向に沿って第１の支持棒９ａと第２の支持棒９ｂが配列され、第１の支持棒９ａと第２の支持棒９ｂは第１の輪状フレーム８１ａの中心に位置するベアリング５ａによって互いに連結されている。そして、第１の輪状フレーム８１ａはベアリング５ａを介して主回転軸３の周りを、主回転軸３とは反対方向に回転する。図５に示すように、第２の輪状フレーム８１ｂの直径方向に沿って第３の支持棒９ｃと第４の支持棒９ｄが配列され、第３の支持棒９ｃと第４の支持棒９ｄは主回転軸３によって互いに連結され、主回転軸３と共に回転する。   As shown in FIGS. 1 and 2, the first rotating body 21a of the power generation apparatus according to the first embodiment includes the first annular frame 81a, and the second rotating body 21b is the second annular frame 81b. Equipped with That is, the first rotating body 21a is arbitrarily selected in the space between the surface to which the uppermost surface of the first rotating body 21a is extended and the surface to which the lowermost surface of the first rotating body 21a is extended. A first annular frame 81a that constitutes a part of the first rotation surface is provided on the outer peripheral side of the first rotation body 21a. Similarly, the second rotating body 21b is arbitrarily selected in a space between a surface to which the uppermost surface of the second rotating body 21b is extended and a surface to which the lowermost surface of the second rotating body 21b is extended. A second ring-shaped frame 81b which constitutes a part of the second rotation surface is provided on the outer peripheral side of the second rotation body 21b. The first support rods 9a and the second support rods 9b are arranged along the diameter direction of the first annular frame 81a, and the first support rods 9a and the second support rods 9b are of the first annular frame 81a. It is mutually connected by the bearing 5a located in the center. Then, the first annular frame 81a rotates around the main rotation shaft 3 in the opposite direction to the main rotation shaft 3 via the bearing 5a. As shown in FIG. 5, the third support rods 9c and the fourth support rods 9d are arranged along the diameter direction of the second annular frame 81b, and the third support rods 9c and the fourth support rods 9d are They are connected to one another by the main axis of rotation 3 and rotate with the main axis of rotation 3.

第１の回転体２１ａの外周点は、図２に示すように、第１の輪状フレーム８１ａの外周側の側面の任意の一点である。同様に、第２の回転体２１ｂの外周点は第２の輪状フレーム８１ｂの外周側の側面の任意の一点となる。第１の回転体２１ａの外周点が描く外周円から定義される第１の回転面と、第２の回転体２１ｂの外周点が描く外周円から定義される第２の回転面とは、互いに平行に対向する関係である。   The outer peripheral point of the first rotating body 21a is, as shown in FIG. 2, an arbitrary point on the outer peripheral side of the first annular frame 81a. Similarly, the outer peripheral point of the second rotating body 21b is an arbitrary point on the outer peripheral side of the second annular frame 81b. The first rotation surface defined by the outer circumference circle drawn by the outer circumference point of the first rotation body 21a and the second rotation surface defined by the outer circumference circle drawn by the outer circumference point of the second rotation body 21b mutually It is a relation facing in parallel.

第１の支持棒９ａには、第１の風受け羽根１１ａが固定され、第２の支持棒９ｂには、第２の風受け羽根１１ｂが固定されている。同様に、第３の支持棒９ｃには、第３の風受け羽根１１ｃが固定され、第４の支持棒９ｄには第４の風受け羽根１１ｄが固定されている。そして、図２においては、第１〜第４の支持棒９ａ〜９ｄ、第１の動力ギア回転軸６１ａ及び第１の対向動力ギア回転軸６１ｂがすべて平行になるように、第１〜第４の支持棒９ａ〜９ｄ、第１〜第４の風受け羽根１１ａ〜１１ｄが位置調整されている。   The first wind receiving blade 11a is fixed to the first support rod 9a, and the second wind receiving blade 11b is fixed to the second support rod 9b. Similarly, the third wind receiving blade 11c is fixed to the third support rod 9c, and the fourth wind receiving blade 11d is fixed to the fourth support rod 9d. And in FIG. 2, the first to fourth supporting rods 9a to 9d, the first power gear rotary shaft 61a and the first opposing power gear rotary shaft 61b are all parallel to one another. The positions of the support rods 9a to 9d and the first to fourth wind receiving blades 11a to 11d are adjusted.

図１に示すように、円筒面をなすベアリング５ａの外周面にＴ字型に直交するように第１の支持棒９ａ及び第２の支持棒９ｂが固定されている。第１の支持棒９ａ及び第２の支持棒９ｂは互いに同一形状であり、長手方向は主回転軸３を挟んで互いに同一直線状に位置する。第１の支持棒９ａの上面端部付近に第１の風受け羽根１１ａが固定され、第２の支持棒９ｂの上面端部付近に第１の風受け羽根１１ａと同一形状の第２の風受け羽根１１ｂが、第１の風受け羽根１１ａとは風受け用の凹部を反対の向きになるように固定されている。第１の風受け羽根１１ａ及び第２の風受け羽根１１ｂの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第１の輪状フレーム８１ａは、上面に放射状の第１の駆動ギアの歯を有し、第１の支持棒９ａ及び第２の支持棒９ｂのそれぞれの外周側の端部に固定されている。第１の回転体２１ａは、風を受けると、ベアリング５ａごと第１方向（図１のＣ及びＤの矢印の方向）に回転する。   As shown in FIG. 1, a first support rod 9a and a second support rod 9b are fixed on the outer peripheral surface of a cylindrical bearing 5a so as to be orthogonal to the T-shape. The first support rods 9a and the second support rods 9b have the same shape, and the longitudinal directions are located on the same straight line with the main rotation shaft 3 interposed therebetween. A first wind receiving blade 11a is fixed near the upper end of the first support rod 9a, and a second wind having the same shape as the first wind receiving blade 11a near the upper end of the second support rod 9b. The receiving blade 11b is fixed so that the recess for receiving the wind is opposite to the first wind receiving blade 11a. The fixed locations of the first wind receiving blade 11 a and the second wind receiving blade 11 b are in a symmetrical positional relationship with respect to the main rotation axis 3. The first annular frame 81a has radial first drive gear teeth on the upper surface, and is fixed to the outer peripheral end of each of the first support rod 9a and the second support rod 9b. When the first rotating body 21a receives the wind, the first rotating body 21a rotates in the first direction (the direction of the arrows C and D in FIG. 1) together with the bearing 5a.

図１及び図５に示すように、主回転軸３の長手方向にＴ字型に直交するように第３の支持棒９ｃ及び第４の支持棒９ｄが固定されている。第３の支持棒９ｃ及び第４の支持棒９ｄは互いに同一形状であり、長手方向は主回転軸３を挟んで互いに同一直線状に位置する。第３の支持棒９ｃ及び第４の支持棒９ｄは第１の回転体２１ａの上方に位置する。第３の支持棒９ｃの上面端部付近に、風を受けると第２の回転体２１ｂが第１の回転体２１ａと逆回転するような方向へ風受け用の凹部を向けて、第１の風受け羽根１１ａと同一形状の第３の風受け羽根１１ｃが固定されている。第４の支持棒９ｄの上面端部付近に、第３の風受け羽根１１ｃとは風受け用の凹部を反対の向きになるように、第１の風受け羽根１１ａと同一形状の第４の風受け羽根１１ｄが固定されている。第３の風受け羽根１１ｃ及び第４の風受け羽根１１ｄの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第２の輪状フレーム８１ｂは、下面に放射状の第２の駆動ギアの歯を有し、第３の支持棒９ｃ及び第４の支持棒９ｄのそれぞれの外周側の端部に固定されている。第２の輪状フレーム８１ｂの中心には主回転軸３が位置する。第２の回転体２１ｂは、風を受けると第２方向（図１のＢ方向）に回転し、その回転と同時に、主回転軸３も第２方向（図１のＡ方向）に回転する。   As shown in FIGS. 1 and 5, the third support rod 9 c and the fourth support rod 9 d are fixed so as to be orthogonal to the T-shape in the longitudinal direction of the main rotation shaft 3. The third support rod 9c and the fourth support rod 9d have the same shape, and the longitudinal directions are located on the same straight line with the main rotation shaft 3 interposed therebetween. The third support rod 9c and the fourth support rod 9d are located above the first rotating body 21a. In the vicinity of the upper surface end of the third support rod 9c, the concave portion for receiving the wind is directed in such a direction that the second rotating body 21b is reversely rotated with the first rotating body 21a when wind is received. A third wind receiving blade 11c having the same shape as the wind receiving blade 11a is fixed. In the vicinity of the upper surface end of the fourth support rod 9 d, the fourth of the same shape as the first wind receiving blade 11 a so that the concave portion for receiving the wind is opposite to the third wind receiving blade 11 c. The wind vane 11d is fixed. The fixing points of the third wind receiving blade 11 c and the fourth wind receiving blade 11 d are in a symmetrical positional relationship with the main rotation axis 3 interposed therebetween. The second annular frame 81b has radial second drive gear teeth on its lower surface, and is fixed to the outer peripheral end of each of the third support rod 9c and the fourth support rod 9d. The main rotation axis 3 is located at the center of the second annular frame 81b. When wind is received, the second rotating body 21b rotates in the second direction (direction B in FIG. 1), and at the same time, the main rotation shaft 3 also rotates in the second direction (direction A in FIG. 1).

図２に示すように、第１の動力ギア３１ａの歯は第１の輪状フレーム８１ａの第１の駆動ギアの歯及び第２の輪状フレーム８１ｂの第２の駆動ギアの歯に垂直にかみ合って回転するように設けられている。風を受けて第１の回転体２１ａ及び第２の回転体２１ｂが回転すると、第１の動力ギア３１ａは図１のＥの矢印の向きに回転する。第１の動力ギア３１ａの回転は第１の動力ギア回転軸６１ａを介して、支柱７aに保持されている第１の発電機６２ａに伝達され、発電が行われる。第１の動力ギア３１ａは、第１の回転体２１ａ及び第２の回転体２１ｂに挟まれ、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の動力ギア３１ａの回転力は大きくなる。   As shown in FIG. 2, the teeth of the first power gear 31a are vertically engaged with the teeth of the first drive gear of the first annular frame 81a and the teeth of the second drive gear of the second annular frame 81b. It is provided to rotate. When the first rotating body 21a and the second rotating body 21b rotate in response to the wind, the first power gear 31a rotates in the direction of the arrow E in FIG. The rotation of the first power gear 31a is transmitted to the first generator 62a held by the support 7a via the first power gear rotary shaft 61a to generate power. Since the first power gear 31a is sandwiched between the first rotating body 21a and the second rotating body 21b and obtains rotational torque from both rotating bodies, the first power gear 31a is more likely than the case of only one rotating body. The rotational force of the power gear 31a is increased.

図２に示すように、第１の動力ギア３１ａと同様、第１の対向動力ギア３１ｂの歯は第１の輪状フレーム８１ａの第１の駆動ギアの歯及び第２の輪状フレーム８１ｂの第２の駆動ギアの歯に垂直にかみ合って回転するように設けられている。風を受けて第１の回転体２１ａ及び第２の回転体２１ｂが回転すると、第１の対向動力ギア３１ｂは図１のＦの矢印の向きに回転する。第１の対向動力ギア３１ｂの回転は第１の対向動力ギア回転軸６１ｂを介して、支柱７ｂに保持されている第１の対向発電機６２ｂに伝達され、発電が行われる。なお、第１の対向発電機６２ｂでの発電は、第１の発電機６２ａの駆動する回転トルクを向上させるためには行わない方が好ましいので、第１の対向発電機６２ｂは無くてもよい。発電機は発電装置全体で少なくとも１つあれば、回転体から得られる回転トルクを伝えられるが、エネルギー保存の法則から、発電機の個数が増えるほど、一つの発電機を駆動する回転トルクが減少するためである。しかし、発電装置の故障防止目的で、第２の回転体２１ｂの重量を均等に分散する必要があるため、少なくとも第１の対向動力ギア３１ｂは第１の動力ギア３１ａと主回転軸３をはさんで対称の位置に配置し、第１の対向動力ギア３１ｂを無負荷とした方がよい。又、図２では第１の回転体２１ａと第２の回転体２１ｂの間に、同一形状、同一サイズの第１の動力ギア３１ａと第１の対向動力ギア３１ｂが対角線上に挟まれた構造を例示しているが、第１の回転体２１ａと第２の回転体２１ｂの間の重力バランスを均等化する目的の為には、１２０度間隔で３個の動力ギアを設けることも、９０度間隔で４個の動力ギアを設けることも設計上可能である。即ち第１の回転体２１ａと第２の回転体２１ｂの間に、３個以上ｋ個（ｋは３以上の正の整数）の動力ギアを、円周上に等間隔に設けることも重力バランスをとる得る点では好ましいが、発電機を駆動する回転トルクを高めるためには、そのうち１個の動力ギアに発電機を接続することが好ましい。なお、第１の対向動力ギア３１ｂも第１の動力ギア３１ａと同様に、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の対向動力ギア３１ｂの回転力は大きくなるので、第１の対向発電機６２ｂで発電を実施した場合にも、一応の効果を奏することが可能である。   As shown in FIG. 2, like the first power gear 31a, the teeth of the first opposing power gear 31b are the teeth of the first drive gear of the first annular frame 81a and the second of the second annular frame 81b. It is provided to rotate in mesh with the teeth of the drive gear. When the first rotating body 21a and the second rotating body 21b rotate in response to the wind, the first opposing power gear 31b rotates in the direction of the arrow F in FIG. The rotation of the first opposing power gear 31b is transmitted to the first opposing generator 62b held by the support 7b via the first opposing power gear rotary shaft 61b to generate power. In addition, since it is preferable not to perform power generation in the first opposing generator 62b in order to improve the rotational torque driven by the first generator 62a, the first opposing generator 62b may be omitted. . If there is at least one generator in the entire generator, the rotational torque obtained from the rotating body can be transmitted, but from the law of energy conservation, the rotational torque for driving one generator decreases as the number of generators increases In order to However, since it is necessary to evenly distribute the weight of the second rotating body 21b for the purpose of preventing a failure of the power generation apparatus, at least the first opposing power gear 31b is configured to have the first power gear 31a and the main rotating shaft 3 It is better to arrange them in symmetrical positions and to make the first opposing power gear 31 b unloaded. Further, in FIG. 2, a structure in which a first power gear 31 a and a first opposing power gear 31 b of the same shape and the same size are diagonally sandwiched between the first rotating body 21 a and the second rotating body 21 b. In order to equalize the balance of gravity between the first rotating body 21a and the second rotating body 21b, it is also possible to provide three power gears at intervals of 120 degrees. It is also possible in design to provide four power gears in degree intervals. That is, it is also possible to provide 3 or more k (k is a positive integer of 3 or more positive) power gears at equal intervals on the circumference between the first rotating body 21a and the second rotating body 21b. In order to increase the rotational torque for driving the generator, it is preferable to connect the generator to one of the power gears. In the same manner as the first power gear 31a, since the first opposing power gear 31b also obtains rotational torque from both rotating bodies, the first opposing power gear 31b can be obtained compared to the case where there is only one rotating body. Since the rotational force is increased, even when power generation is performed by the first opposing generator 62b, it is possible to obtain a certain effect.

更に、図２において、正面側から風が吹いたと仮定すると、第２の風受け羽根１１ｂ及び第３の風受け羽根１１ｃは風を受け、第１の風受け羽根１１ａ及び第４の風受け羽根１１ｄは風を上下に受け流すことになる。第１の風受け羽根１１ａが上方に受け流した風の一部は、第３の風受け羽根１１ｃが受ける。第４の風受け羽根１１ｄが下方に受け流した風の一部は、第２の風受け羽根１１ｂが受ける。第２の風受け羽根１１ｂ及び第３の風受け羽根１１ｃが受ける風量は、第１の風受け羽根１１ａ及び第４の風受け羽根１１ｄがない時と比べ、受け流されてきた風の分、多くなる。これにより、第１の回転体２１ａ及び第２の回転体２１ｂはより速く回転することができ、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂに付与する回転トルクが大きくなる。   Furthermore, in FIG. 2, assuming that the wind is blown from the front side, the second wind receiving blade 11b and the third wind receiving blade 11c receive the wind, and the first wind receiving blade 11a and the fourth wind receiving blade 11d will be able to receive the wind up and down. The third wind receiving blade 11 c receives a part of the wind which the first wind receiving blade 11 a has flowed upward. The second wind receiving blade 11 b receives part of the wind that the fourth wind receiving blade 11 d has flowed downward. The amount of wind received by the second wind receiving blade 11b and the third wind receiving blade 11c is a portion of the received wind compared to when the first wind receiving blade 11a and the fourth wind receiving blade 11d are not provided, Become more. As a result, the first rotating body 21a and the second rotating body 21b can rotate faster, and the rotational torque to be applied to the first power gear 31a and the first opposing power gear 31b becomes larger.

図３の拡大図に示すように、第１の動力ギア３１ａの歯は、第１の駆動ギアの歯７１ａ１、７１ａ２、・・・及び第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・に垂直にかみ合っている。第１の輪状フレーム８１ａの上面には第１の駆動ギアの歯７１ａ１、７１ａ２、・・・が第１の輪状フレーム８１ａと一体となる形で設けられ、第２の輪状フレーム８１ｂの下面には第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・が第２の輪状フレーム８１ｂと一体となる形で設けられている。風を受けると、図４の断面図に示す第１の輪状フレーム８１ａは図４に向かって左方向、第２の輪状フレーム８１ｂは図４に向かって右方向に動く。第１の動力ギア３１ａの歯と、第１の駆動ギアの歯７１ａ１、７１ａ２、・・・及び第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・はかみ合うので、第１の輪状フレーム８１ａ及び第２の輪状フレーム８１ｂが動くに伴い、第１の動力ギア３１ａは第１の動力ギア回転軸６１ａを軸として図４のＡ方向に回転する。 As shown in the enlarged view of FIG. 3, the teeth of the first power gear 31a is tooth 71a 1 of the first driving gear, 71a 2, teeth 71b 1 ... and the second drive gear, 71b 2, ... vertically engaged. The first drive gear teeth 71a 1 , 71a 2 ,... Are provided integrally with the first annular frame 81a on the upper surface of the first annular frame 81a, and the lower surface of the second annular frame 81b The teeth 71b 1 , 71b 2 ,... Of the second drive gear are provided integrally with the second annular frame 81b. When wind is received, the first annular frame 81a shown in the cross-sectional view of FIG. 4 moves to the left in FIG. 4, and the second annular frame 81b moves to the right in FIG. The teeth of the first power gear 31a, the teeth 71a 1 of the first driving gear, 71a 2, teeth 71b 1 ... and the second drive gear, 71b 2, since ... meshes, first As the ring-shaped frame 81a and the second ring-shaped frame 81b move, the first power gear 31a rotates about the first power gear rotary shaft 61a in the direction A in FIG.

第１の動力ギア３１ａには、図６（ａ）に示すように、上面４４ａと下面４４ｂを有し、一定の厚み（歯幅）の歯を外周の側面に等間隔に有する平歯車タイプを用いることができる。平歯車は、その回転軸に対して平行な歯すじの歯を有する。比較的容易に製作される歯車であり、他の歯車と組み合わされて主に平行な軸間の動力の伝達に用いられる。図６（ａ）及び（ｂ）に示すように、第１の動力ギア３１ａの歯は、歯先面４２ｉとその歯先面４２ｉの両側に接する第１の歯面４３ｉａ及び第２の歯面４３ｉｂで囲まれた部位である。第１の動力ギア３１ａの歯と歯の間には歯底面４１ｉがある。ここで、歯底面、歯先面、第１の歯面及び第２の歯面の符号の下付き添え字「ｉ」には１以上の整数が入り、最大数は動力ギアの歯数と一致する。上面４４ａと下面４４ｂとは互いに平行で同一形状であり、それらと歯底面４１ｉ、歯先面４２ｉ、第１の歯面４３ｉａ及び第２の歯面４３ｉｂはそれぞれ垂直に接している。図示を省略しているが、第１の対向動力ギア３１ｂも同様の構造である。第１の動力ギア３１ａの歯の形状は、歯車全体の大きさ等から数学的な計算で求められる曲線、すなわち歯形曲線が基となって決められる。歯形曲線には、一般にインボリュート曲線が用いられるが、他の曲線、例えばサイクロイド曲線等を用いてもよい。歯数は、かみ合わせる他方の歯車の歯にかみ合うよう、任意に設定することができる。 As shown in FIG. 6A, the first power gear 31a has a spur gear type having an upper surface 44a and a lower surface 44b, and having teeth of a constant thickness (tooth width) on the side of the outer periphery at equal intervals. It can be used. The spur gear has teeth of teeth parallel to its rotational axis. It is a gear that is relatively easy to manufacture, and is used in combination with other gears to transmit power between mainly parallel axes. Figure 6 As shown in (a) and (b), the teeth of the first power gear 31a is tooth crest 42 i and the first tooth surface in contact with both sides of the tooth crest 42 i 43 ia and second Of the tooth surface 43 ib . Between the teeth of the first power gear 31a is root surface 41 i. Here, the suffixes " i " of the symbols of the tooth base, tooth tip, first tooth surface and second tooth surface contain integers of 1 or more, and the maximum number matches the number of teeth of the power gear Do. The upper surface 44a and the lower surface 44b are parallel to each other and have the same shape, and they are in contact with the bottom surface 41 i , the tooth top surface 42 i , the first tooth surface 43 ia and the second tooth surface 43 ib vertically. . Although illustration is omitted, the first opposing power gear 31 b also has the same structure. The shape of the teeth of the first power gear 31a is determined based on a curve obtained by mathematical calculation from the size of the entire gear, etc., that is, a tooth profile curve. Generally, an involute curve is used as a tooth profile curve, but another curve such as a cycloid curve may be used. The number of teeth can be arbitrarily set to mesh with the teeth of the other gear to be meshed.

第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂの素材としては、炭素鋼や炭素合金鋼、球状黒鉛鋳鉄、ステンレス鋼、特殊プラスチック等、様々な素材が使用可能である。一般に歯車を継続使用すると、歯元疲労や歯面疲労、曲げ疲労などによる疲労破壊が起こるため、それらが起こりにくいような素材を選ぶことが望ましい。流体力として水力や潮汐力を用いる場合は、水や塩分などによる影響を居慮し、耐水性や耐腐食性に優れた素材を用い、あるいは耐水性や耐腐食性に富んだ素材で表面をコーティングすることが望ましい。   As materials of the first power gear 31a and the first opposing power gear 31b, various materials such as carbon steel, carbon alloy steel, spheroidal graphite cast iron, stainless steel, special plastic and the like can be used. In general, when a gear is continuously used, fatigue failure occurs due to tooth root fatigue, tooth surface fatigue, bending fatigue and the like, so it is desirable to select a material that is less likely to occur. When hydraulic power or tidal power is used as the fluid power, the effect of water or salt is taken into consideration, a material excellent in water resistance or corrosion resistance is used, or the surface is made of a material excellent in water resistance or corrosion resistance. It is desirable to coat.

図６（ａ）に示す第１の動力ギア３１ａの歯にかみ合う第１の駆動ギアの歯を有する第１の輪状フレーム８１ａは、図７の斜視図に示すように、上面に放射状で等間隔に第１の駆動ギアの歯７１ａ１、７１ａ２、・・・を設けている。形状が王冠に似ていることから、このタイプの歯車は「冠歯車」と呼ばれ、平歯車と組み合せると回転軸の方向を９０°変えることができる。第１の駆動ギアの歯７１ａ１、７１ａ２、・・・は第１の輪状フレーム８１ａと一体となった構造でもよいし、第１の輪状フレーム８１ａに後から第１の駆動ギアの歯７１ａ１、７１ａ２、・・・を取り付けてもよい。第１の駆動ギアの歯７１ａ１、７１ａ２、・・・はそれぞれ、第１の輪状フレーム８１ａの外周に近いほど高さを増す凸部である。第１の輪状フレーム８１ａの第１の駆動ギアの歯７１ａ１、７１ａ２、・・・についても、第１の動力ギア３１ａと同様に、歯が疲労破壊されないような素材を各種選ぶことが望ましい。第２の駆動ギアを有する第２の輪状フレーム８１ｂにも、下面方向から見た斜視図が上下反転させた図７と同様の冠歯車タイプを用いることができる。 As shown in the perspective view of FIG. 7, the first annular frame 81a having the teeth of the first drive gear meshing with the teeth of the first power gear 31a shown in FIG. teeth 71a 1 of the first driving gear, 71a 2, provided ... are in. Similar in shape to a crown, this type of gear is called a "crown gear" and when combined with a spur gear, can change the direction of the rotation axis by 90 °. The first drive gear teeth 71a 1 , 71a 2 ,... May be integrated with the first annular frame 81a, or the first annular gear 81a may have a first drive gear tooth 71a. 1 , 71 a 2 , ... may be attached. The teeth 71a 1 , 71a 2 ,... Of the first drive gear are convex portions that increase in height closer to the outer periphery of the first annular frame 81a. As for the first drive gear teeth 71a 1 , 71a 2 ,... Of the first annular frame 81a, as in the first power gear 31a, it is desirable to select various materials that do not cause fatigue fracture of the teeth. . As the second annular frame 81b having the second drive gear, it is possible to use a crown gear type similar to FIG. 7 in which a perspective view seen from the lower surface direction is upside down.

第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂには平歯車以外の種類の歯車、例えばはすば歯車やかさ歯車等を使用することができる。はすば歯車は、平歯車の歯を歯車の軸に対して斜めに配置し、螺旋状とした歯車である。同時にかみ合う歯数を増やし、歯当たりが分散されるので音が静かで、回転トルクの変動が少ないという利点がある。かさ歯車は円錐面上に歯が刻まれ、広げた傘のような形状の歯車である。かさ歯車は、平行な軸ではなく、垂直に交わるような角度がついた軸の間での動力の伝達に適している。   For the first power gear 31a and the first opposing power gear 31b, gears of types other than spur gears, for example, helical gears or bevel gears can be used. The helical gear is a helical gear in which the teeth of the spur gear are disposed obliquely to the axis of the gear. At the same time, the number of meshing teeth is increased, and the tooth contact is dispersed, so that there is an advantage that the sound is quiet and the fluctuation of the rotational torque is small. A bevel gear is a gear with an umbrella-like shape with teeth carved on a conical surface. The bevel gears are suitable for the transmission of power between axes that are not perpendicular but angled perpendicular to one another.

第１の動力ギア３１ａには、図８（ａ）の斜視図に示すように、外周の側面に歯を等間隔に有するが、上面４４ａに対して下面４４ｂの方の面積が大きく、上面４４ａと下面４４ｂとをつなぐように、歯底面４１ｉ、歯先面４２ｉ、第１の歯面４３ｉａ及び第２の歯面４３ｉｂが配置するかさ歯車タイプを用いることができる。図８（ａ）に示す第１の動力ギア３１ａは、平歯車を円錐状に窄めたような形状であり、歯すじが円錐形の頂点を目指す直線形状であるので、かさ歯車の中でも「すぐばかさ歯車」に分類される。すぐばかさ歯車は比較的に製作が容易であるため、動力伝達用かさ歯車として最も普及しているタイプである。図８（ａ）及び（ｂ）に示すように、歯は、歯先面４２ｉとその歯先面４２ｉの両側に接する第１の歯面４３ｉａ及び第２の歯面４３ｉｂで囲まれた部位である。歯と歯の間には歯底面４１ｉがある。上面４４ａと下面４４ｂとは互いに平行であり、下面４４ｂから上面４４ａにかけてテーパをつけるように、歯底面４１ｉ、歯先面４２ｉ、第１の歯面４３ｉａ及び第２の歯面４３ｉｂが接している。図示を省略しているが、第１の対向動力ギア３１ｂも同様の構造である。 In the first power gear 31a, as shown in the perspective view of FIG. 8A, the teeth are equally spaced on the side of the outer periphery, but the area of the lower surface 44b is larger than the upper surface 44a. It is possible to use a bevel gear type in which the tooth base 41 i , the tooth top 42 i , the first tooth surface 43 ia and the second tooth surface 43 ib are arranged so as to connect the lower surface 44 b with the lower surface 44 b. The first power gear 31a shown in FIG. 8 (a) has a shape in which the spur gear is narrowed in a conical shape, and the tooth lines have a linear shape aiming at the apex of the conical shape. It is classified as a straight bevel gear. A straight bevel gear is the most popular type of bevel gear for power transmission because it is relatively easy to manufacture. As shown in FIG. 8 (a) and (b), teeth, surrounded by the first tooth surface 43 ia and the second tooth surface 43 ib in contact with both sides of the tooth crest 42 i and the tooth crest 42 i Site. Between the teeth there is a tooth bottom 41 i. Are mutually parallel and the upper surface 44a and lower surface 44b, as tapering from the bottom surface 44b toward the upper surface 44a, bottom land 41 i, tooth crest 42 i, the first tooth surface 43 ia and the second tooth surface 43 ib I am in contact with you. Although illustration is omitted, the first opposing power gear 31 b also has the same structure.

図８（ａ）に示す第１の動力ギア３１ａにかみ合う第１の駆動ギアを有する第１の輪状フレーム８１ａは、図９の斜視図に示すように、上面に放射状で等間隔に第１の駆動ギアの歯７１ａ１、７１ａ２、・・・を有するすぐばかさ歯車である。第１の駆動ギアの歯７１ａ１、７１ａ２、・・・自体の厚みは一定であるが、第１の輪状フレーム８１ａの全体の厚みは、外周に近くなるほど薄くなる。第２の駆動ギアを有する第２の輪状フレーム８１ｂにも、下面方向から見た斜視図が上下反転させた図９と同様のすぐばかさ歯車タイプを用いることができる。第２の輪状フレーム８１ｂは、図１０に示すように、下面に第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・を有し、第１の動力ギア３１ａとかみ合っている。図１１に示すように、第１の動力ギア３１ａの歯及び第１の駆動ギアの歯７１ａ１、７１ａ２、・・・は、それぞれの歯車の円錐形の頂点を内側に向けるようにかみ合って回転する。第１の駆動ギアａを有する第１の輪状フレーム８１ａが図１１のＡ方向に動くと第１の動力ギア３１ａはＢ方向に回転することになる。図示は省略するが、第２の駆動ギアを有する第２の輪状フレーム８１ｂは、第２の駆動ギアを第１の駆動ギアと対向させるように、第１の輪状フレーム８１ａと平行に位置し、図１１の第１の輪状フレーム８１ａのＡ方向とは逆方向に回転し、図１１のＢ方向に回転する第１の動力ギア３１ａとかみ合うことになる。 A first annular frame 81a having a first drive gear meshing with a first power gear 31a shown in FIG. 8A is, as shown in the perspective view of FIG. It is a straight bevel gear with drive gear teeth 71a 1 , 71a 2 . Although the thickness of the teeth 71a 1 , 71a 2 ,... Of the first drive gear is constant, the overall thickness of the first annular frame 81a becomes thinner toward the outer periphery. As the second annular frame 81b having the second drive gear, it is possible to use a straight bevel gear type similar to FIG. 9 in which the perspective view seen from the lower surface direction is upside down. As shown in FIG. 10, the second annular frame 81 b has teeth 71 b 1 , 71 b 2 ,... Of the second drive gear on the lower surface, and is meshed with the first power gear 31 a. As shown in FIG. 11, the teeth of the first power gear 31 a and the teeth 71 a 1 , 71 a 2 ,... Of the first drive gear are engaged such that the apexes of the cones of the respective gears are directed inward. Rotate. When the first annular frame 81a having the first drive gear a moves in the A direction of FIG. 11, the first power gear 31a rotates in the B direction. Although not shown, the second annular frame 81b having the second drive gear is positioned parallel to the first annular frame 81a so that the second drive gear faces the first drive gear, The first ring-shaped frame 81a of FIG. 11 rotates in the direction opposite to the A direction, and meshes with the first power gear 31a rotating in the B direction of FIG.

第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂには、すぐばかさ歯車以外にも、まがりばかさ歯車やゼロールかさ歯車等の他のかさ歯車を使用することができる。「まがりばかさ歯車」は、はすば歯車を円錐状に窄め、かつ、歯すじを直線ではなく曲線（円弧）状にした形状である。すぐばかさ歯車より製作は難しいが、歯当たり面積が広いので強度が増し、耐久性にも優れ、回転が静かであるという特徴があり、自動車、船舶、車両等、高速運転をするような機械の最終減速装置に利用されている。「ゼロールかさ歯車」は、平歯車を円錐状に窄め、かつ、歯すじを直線ではなく曲線（円弧）状にした形状であり、まがりばかさ歯車の歯すじのねじれがないタイプである。ゼロールかさ歯車は、すぐばかさ歯車とまがりばかさ歯車の特徴を併せ持ち、すぐばかさ歯車に比べて、滑らかな運動が可能である。   Besides the straight bevel gears, other bevel gears such as spiral bevel gears or zero roll bevel gears can be used for the first power gear 31 a and the first opposing power gear 31 b. The "round bevel gear" has a shape in which the helical gear is conically narrowed and the teeth are not straight but curved (arc). It is more difficult to manufacture than straight bevel gears, but it is characterized by greater strength and durability due to its wide tooth contact area, excellent rotation and quiet rotation, and machines that operate at high speeds, such as automobiles, ships, and vehicles. Is used for the final reduction gear. The "Zerol bevel gear" is a type in which the spur gear is conically shaped and the teeth are not straight but curved (arc), and there is no twist in the spiral bevel gear teeth. The zero roll bevel gear combines the features of a straight bevel gear and a spiral bevel gear, and allows smooth movement as compared to the straight bevel gear.

式（１）で示したように、ファラデーの電磁誘導の法則によれば、発電機の開放電圧は発電機の回転数に依存し、低速回転では発電機の極数が多い方が有利であり、高速回転では発電機の極数が少ない方が有利である。低速回転で発電する場合は極数が多い方が有利であるが、極数が多くなると内部抵抗が増え、大きな回転トルクが必要になる。第１の実施の形態に係る発電装置によれば、第１の動力ギア３１ａは、第１の回転体２１ａ及び第２の回転体２１ｂの両方から回転トルクを得ることができるので、多極発電機を用いることによって、風力が弱い環境でも発電機の回転トルクを大きくすることができるので、効率よく安定した発電をすることができる。   As shown in equation (1), according to Faraday's law of electromagnetic induction, the open circuit voltage of the generator depends on the number of revolutions of the generator, and at low speed rotation, it is advantageous to have more generator poles. For high-speed rotation, it is advantageous for the number of generator poles to be small. When generating electricity at low speed, it is advantageous that the number of poles is large, but when the number of poles is large, internal resistance increases and a large rotational torque is required. According to the power generation apparatus according to the first embodiment, the first power gear 31a can obtain rotational torque from both the first rotating body 21a and the second rotating body 21b, so multipolar power generation can be achieved. By using the machine, the rotational torque of the generator can be increased even in an environment where wind power is weak, so efficient and stable power generation can be performed.

＜第１の実施の形態の変形例＞
図１２に示すように、第１の実施の形態の変形例に係る発電装置は、図２の構造に加え、図２に示した第１の回転体２１ａ及び第２の回転体２１ｂとそれぞれ同一の構造である第３の回転体２１ｃ及び第４の回転体２１ｄを更に備えた多層構造である。この第１の実施の形態の変形例に係る発電装置においては、第２の回転体２１ｂ及び第３の回転体２１ｃの両者から回転トルクを付与される第２の動力ギア３１ｃ及び第２の対向動力ギア３１ｄと，第３の回転体２１ｃ及び第４の回転体２１ｄの両者から回転トルクを付与される第３の動力ギア３１ｅ及び第３の対向動力ギア３１ｆとを更に備える。 <Modification of First Embodiment>
As shown in FIG. 12, the power generation apparatus according to the modification of the first embodiment is the same as the first rotary body 21a and the second rotary body 21b shown in FIG. 2 in addition to the structure of FIG. The multi-layer structure further includes a third rotating body 21c and a fourth rotating body 21d having a structure of In the power generation apparatus according to the modification of the first embodiment, the second power gear 31c and the second opposing face to which rotational torque is applied from both the second rotating body 21b and the third rotating body 21c. The power gear 31 d further includes a third power gear 31 e and a third opposing power gear 31 f to which rotational torque is applied from both of the third rotating body 21 c and the fourth rotating body 21 d.

第１の実施の形態の変形例に係る発電装置においては、第２の動力ギア３１ｃ及び第２の対向動力ギア３１ｄを駆動するように、第２の輪状フレーム８１ｂの上面に第３の駆動ギアが設けられ、第３の輪状フレーム８１ｃの下面には第４の駆動ギアが設けられている。同様に、第３の動力ギア３１ｅ及び第３の対向動力ギア３１ｆを駆動するように、第３の輪状フレーム８１ｃの上面に第５の駆動ギアが設けられ、第４の輪状フレーム８１ｄの下面には第６の駆動ギアが設けられている。第２の動力ギア３１ｃ、第２の対向動力ギア３１ｄ、第３の動力ギア３１ｅ及び第３の対向動力ギア３１ｆのそれぞれに対応して、第２の発電機６２ｃ、第２の対向発電機６２ｄ，第３の発電機６２ｅ及び第３の対向発電機６２ｆが更に設けられている。第２の発電機６２ｃ及び第３の発電機６２ｅは支柱７aに保持され、第２の対向発電機６２ｄ及び第３の対向発電機６２ｆは支柱７ｂに保持されている。   In the power generation apparatus according to the modification of the first embodiment, the third drive gear is provided on the upper surface of the second annular frame 81b so as to drive the second power gear 31c and the second opposing power gear 31d. And a fourth drive gear is provided on the lower surface of the third annular frame 81c. Similarly, a fifth drive gear is provided on the upper surface of the third annular frame 81c so as to drive the third power gear 31e and the third opposing power gear 31f, and the lower surface of the fourth annular frame 81d is provided. A sixth drive gear is provided. A second generator 62c and a second opposing generator 62d corresponding to the second power gear 31c, the second opposing power gear 31d, the third power gear 31e, and the third opposing power gear 31f, respectively. , A third generator 62e and a third opposing generator 62f are further provided. The second generator 62c and the third generator 62e are held by the support 7a, and the second opposed generator 62d and the third opposed generator 62f are held by the support 7b.

第２の動力ギア３１ｃの回転は第２の動力ギア回転軸６１ｃを介して第２の発電機６２ｃに伝達される。同様に、第２の対向動力ギア３１ｄの回転は第２の対向動力ギア回転軸６１ｄを介して第２の対向発電機６２ｄに、第３の動力ギア３１ｅの回転は第３の動力ギア回転軸６１ｅを介して第３の発電機６２ｅに、第３の対向動力ギア３１ｆの回転は第３の対向動力ギア回転軸６１ｆを介して第３の対向発電機６２ｆに伝達される。なお、第２の対向発電機６２ｄ及び第３の対向発電機６２ｆによる発電は、第２の発電機６２ｃ、第３の発電機６２ｅをそれぞれ駆動する回転トルクを高めるためには行わない方が好ましく、第２の対向発電機６２ｄ及び第３の対向発電機６２ｆは無くてもよいことは、第１の対向発電機６２ｂについて述べたのと同様である。又、第２の回転体２１ｂと第３の回転体２１ｃの間に、ｋ個の動力ギアを円周上に等間隔に設け、同様に、第３の回転体２１ｃと第４の回転体２１ｄの間にｋ個の動力ギアを円周上に等間隔に設けて、それぞれの層における回転体同士の重力バランスをとるようにしてもよい。その場合、特定の発電機を駆動する回転トルクを高めるためには、それぞれの層における回転体の間に存在する１個の動力ギアに発電機を接続することが好ましいが、それぞれの層の発電機の位置は同一鉛直線上に配列される必要性はない。   The rotation of the second power gear 31c is transmitted to the second generator 62c via the second power gear rotary shaft 61c. Similarly, the rotation of the second opposing power gear 31d is transmitted to the second opposing generator 62d via the second opposing power gear rotary shaft 61d, and the rotation of the third power gear 31e is the third power gear rotary shaft. The rotation of the third opposing power gear 31f is transmitted to the third generator 62e via the third opposing power gear rotating shaft 61f via the third generator 62e via 61e. The power generation by the second opposing generator 62d and the third opposing generator 62f is preferably not performed to increase the rotational torque for driving the second generator 62c and the third generator 62e, respectively. The second opposing generator 62d and the third opposing generator 62f may be omitted as in the case of the first opposing generator 62b. Further, k power gears are provided at equal intervals on the circumference between the second rotating body 21b and the third rotating body 21c, and similarly, the third rotating body 21c and the fourth rotating body 21d are similarly provided. The k power gears may be provided at equal intervals along the circumference to balance the gravity of the rotating bodies in each layer. In that case, in order to increase the rotational torque for driving a specific generator, it is preferable to connect the generator to one power gear existing between the rotating bodies in each layer, but the power generation of each layer is preferable. The positions of the aircraft do not have to be arranged on the same vertical line.

既に述べたように、発電機の開放電圧は発電機の回転数に依存し、低速回転で発電する場合は極数が多い方が有利である。しかし、発電機の極数が多くなると内部抵抗が増え、大きな回転トルクが必要になる。第１の実施の形態の変形例に係る発電装置においては、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂは、第１の回転体２１ａ及び第２の回転体２１ｂの両方から回転トルクを得ることができる。又、第２の動力ギア３１ｃ及び第２の対向動力ギア３１ｄは、第２の回転体２１ｂ及び第３の回転体２１ｃの両方から回転トルクを得ることができる。更に、第３の動力ギア３１ｅ及び第３の対向動力ギア３１ｆは、第３の回転体２１ｃ及び第４の回転体２１ｄの両方から回転トルクを得ることができる。よって、第１の実施の形態の変形例に係る発電装置によれば、多極発電機を有効に活用することが可能になり、風力が弱い環境でも発電機の回転トルクを大きくすることができ、効率よく安定した発電をすることができる。   As described above, the open circuit voltage of the generator depends on the number of revolutions of the generator, and in the case of low speed rotation, it is advantageous to have a large number of poles. However, as the number of generator poles increases, internal resistance increases and a large rotational torque is required. In the power generation apparatus according to the modification of the first embodiment, the first power gear 31a and the first opposing power gear 31b have rotational torque from both the first rotating body 21a and the second rotating body 21b. You can get The second power gear 31c and the second opposing power gear 31d can obtain rotational torque from both the second rotating body 21b and the third rotating body 21c. Furthermore, the third power gear 31 e and the third opposing power gear 31 f can obtain rotational torque from both the third rotating body 21 c and the fourth rotating body 21 d. Therefore, according to the power generation apparatus according to the modification of the first embodiment, it is possible to effectively utilize the multipolar generator, and it is possible to increase the rotational torque of the generator even in an environment where wind power is weak. Can efficiently and stably generate power.

図１２において、正面側から風が吹いたと仮定すると、第２の風受け羽根１１ｂ、第３の風受け羽根１１ｃ、第６の風受け羽根１１ｆ及び第７の風受け羽根１１ｇは風を受け、第１の風受け羽根１１ａ、第４の風受け羽根１１ｄ、第５の風受け羽根１１e及び第８の風受け羽根１１ｈは風を上下に受け流すことになる。第１の風受け羽根１１ａが上方に受け流した風の一部は、第３の風受け羽根１１ｃが受ける。第４の風受け羽根１１ｄが下方に受け流した風の一部は、第２の風受け羽根１１ｂが受け、第４の風受け羽根１１ｄが上方に受け流した風の一部は、第６の風受け羽根１１ｆが受ける。第５の風受け羽根１１eが上方に受け流した風の一部は、第７の風受け羽根１１ｇが受け、第５の風受け羽根１１eが下方に受け流した風の一部は、第３の風受け羽根１１ｃが受ける。第８の風受け羽根１１ｈが下方に受け流した風の一部は、第６の風受け羽根１１ｆが受ける。   In FIG. 12, assuming that the wind is blown from the front side, the second wind receiving blade 11b, the third wind receiving blade 11c, the sixth wind receiving blade 11f and the seventh wind receiving blade 11g receive the wind, The first wind receiving blade 11a, the fourth wind receiving blade 11d, the fifth wind receiving blade 11e and the eighth wind receiving blade 11h receive the wind up and down. The third wind receiving blade 11 c receives a part of the wind which the first wind receiving blade 11 a has flowed upward. A part of the wind received by the fourth wind receiving blade 11d downward is received by the second wind receiving blade 11b, and a part of the wind received by the fourth wind receiving blade 11d upward is the sixth wind Receiving blade 11f receives it. A portion of the wind received by the fifth wind receiving blade 11e upward is received by the seventh wind receiving blade 11g, and a portion of the wind received downward by the fifth wind receiving blade 11e is the third wind Receiving blade 11c receives it. A part of the wind that the eighth wind receiving blade 11 h flows downward is received by the sixth wind receiving blade 11 f.

このため、第１の実施の形態の変形例に係る発電装置によれば、第２の風受け羽根１１ｂ、第３の風受け羽根１１ｃ、第６の風受け羽根１１ｆ及び第７の風受け羽根１１ｇが受ける風量は、第１の風受け羽根１１ａ、第４の風受け羽根１１ｄ、第５の風受け羽根１１e及び第８の風受け羽根１１ｈがない時と比べ、受け流されてきた風の分、多くなる。これにより、第１の回転体２１ａ、第２の回転体２１ｂ、第３の回転体２１ｃ及び第４の回転体２１ｄはより速く回転することができ、第１の動力ギア３１ａ、第１の対向動力ギア３１ｂ、第２の動力ギア３１ｃ、第２の対向動力ギア３１ｄ、第３の動力ギア３１ｅ及び第３の対向動力ギア３１ｆに付与する回転トルクが大きくなる。よって、第１の実施の形態の変形例に係る発電装置によれば、多極発電機を用いて、風力が弱い環境でも発電機の回転トルクを大きくすることができ、効率よく安定した発電をして自然エネルギーを有効利用することができる。図１２では回転体が４層の場合を便宜上例示したが、回転体を３層以上のｎ層（ｎは３以上の正の整数）の多層構造にすることで、動力ギア、対向動力ギア、発電機及び対向発電機の設置個数をそれぞれ（ｎ−１）個に増やすことができ、風力が弱い環境でも発電量を増やすことができ、効率よく安定した自然エネルギーの利用が可能になる。   Therefore, according to the power generation device according to the modification of the first embodiment, the second wind receiving blade 11b, the third wind receiving blade 11c, the sixth wind receiving blade 11f, and the seventh wind receiving blade The amount of wind received by 11 g is greater than that in the case where the first wind receiving blade 11 a, the fourth wind receiving blade 11 d, the fifth wind receiving blade 11 e, and the eighth wind receiving blade 11 h are absent. Minutes will increase. As a result, the first rotating body 21a, the second rotating body 21b, the third rotating body 21c, and the fourth rotating body 21d can rotate faster, and the first power gear 31a is opposed to the first rotating gear 21a. The rotational torque applied to the power gear 31b, the second power gear 31c, the second opposing power gear 31d, the third power gear 31e, and the third opposing power gear 31f is increased. Therefore, according to the power generation apparatus according to the modification of the first embodiment, the rotational torque of the generator can be increased even in an environment where wind power is weak using a multipolar generator, and efficient and stable power generation. And natural energy can be used effectively. In FIG. 12, although the case where the number of rotating bodies is four is exemplified for the sake of convenience, the power gear, the opposing power gear, and the like are formed by forming the rotating body into a multilayer structure of n layers of three or more layers (n is a positive integer of 3 or more). The number of installed generators and the opposite generator can be respectively increased to (n-1), the amount of power generation can be increased even in an environment where wind power is weak, and efficient and stable utilization of natural energy becomes possible.

（第２の実施の形態）
図１３及び図１４に示すように、本発明の第２の実施の形態に係る発電装置は、主回転軸３と、流体力（風力）により主回転軸３の周りを第１方向に回転する第１の回転体２２ａと、第１の回転体２２ａが定義する第１の回転面と平行に対向する第２の回転面を有し、第２の回転面が第１方向と反対の第２方向に、流体力（風力）により主回転軸３の周りを回転する第２の回転体２２ｂを備える。第２の実施の形態に係る発電装置は更に、第１の回転体２２ａ及び第２の回転体２２ｂの両者によって回転トルクが付与されて回転する第１の動力ギア３１ａと、第１の動力ギア３１ａの回転によって駆動される第１の発電機６２ａを備える。第１及び第２の回転面の定義は第１の実施の形態と同様である。 Second Embodiment
As shown in FIGS. 13 and 14, the power generation apparatus according to the second embodiment of the present invention rotates in the first direction around the main rotation shaft 3 by the main rotation shaft 3 and fluid force (wind force) A second rotating surface opposite to the first rotating surface defined by the first rotating body 22a and the first rotating surface defined by the first rotating body 22a, the second rotating surface being opposite to the first direction In the direction, the second rotating body 22 b is provided to rotate around the main rotation axis 3 by fluid force (wind force). The power generation apparatus according to the second embodiment further includes a first power gear 31a that is rotated by applying rotational torque by both the first rotating body 22a and the second rotating body 22b, and a first power gear 31a. A first generator 62a driven by the rotation of 31a is provided. The definitions of the first and second rotation surfaces are the same as in the first embodiment.

図１３の斜視図に示すように、主回転軸３は土台１に据え付けられ、重力方向に直立し、第２方向に回転する。土台１の内部には、主回転軸３の回転エネルギーを取り出すための発電機が設置されていてもよい。図１３及び図１４に示すように、第２の実施の形態に係る発電装置の第１の回転体２２ａは第１の輪状フレーム８１ａ及び第１の保持リング８２ａを備え、第２の回転体２２ｂは第２の輪状フレーム８１ｂ及び第２の保持リング８２ｂを備える。   As shown in the perspective view of FIG. 13, the main rotary shaft 3 is mounted on the base 1, stands upright in the direction of gravity, and rotates in the second direction. A generator for extracting rotational energy of the main rotation shaft 3 may be installed inside the base 1. As shown in FIGS. 13 and 14, the first rotating body 22a of the power generation apparatus according to the second embodiment includes the first annular frame 81a and the first holding ring 82a, and the second rotating body 22b. Comprises a second annular frame 81b and a second retaining ring 82b.

第１の保持リング８２ａの直径方向に沿って第１の支持棒９ａと第２の支持棒９ｂが配列され、第１の支持棒９ａと第２の支持棒９ｂは第１の保持リング８２ａの中心に位置する第１のベアリング５ａによって互いに連結されている。第１の輪状フレーム８１ａの直径方向に沿って第３の支持棒９ｃと第４の支持棒９ｄが配列され、第３の支持棒９ｃと第４の支持棒９ｄは第１の輪状フレーム８１ａの中心に位置する第２のベアリング５ｂによって互いに連結されている。そして、第１の保持リング８２ａは第１のベアリング５ａを介して、第１の輪状フレーム８１ａは第２のベアリング５ｂを介して、主回転軸３の周りを、主回転軸３とは反対方向である第１方向に回転する。第２の輪状フレーム８１ｂの直径方向に沿って第５の支持棒９ｅと第６の支持棒９ｆが配列され、第５の支持棒９ｅと第６の支持棒９ｆは主回転軸３によって互いに連結され、主回転軸３と共に回転する。第２の保持リング８２ｂの直径方向に沿って第７の支持棒９ｇと第８の支持棒９ｈが配列され、第７の支持棒９ｇと第８の支持棒９ｈは主回転軸３によって互いに連結され、主回転軸３と共に回転する。   The first support rods 9a and the second support rods 9b are arranged along the diametrical direction of the first retention ring 82a, and the first support rods 9a and the second support rods 9b are of the first retention ring 82a. It is mutually connected by the 1st bearing 5a located in the center. The third support rods 9c and the fourth support rods 9d are arranged along the diameter direction of the first annular frame 81a, and the third support rods 9c and the fourth support rods 9d are of the first annular frame 81a. It is mutually connected by the 2nd bearing 5b located in the center. The first holding ring 82a passes the first bearing 5a, and the first annular frame 81a passes the second bearing 5b, around the main rotation shaft 3 in the direction opposite to the main rotation shaft 3 Rotate in the first direction. The fifth support rod 9e and the sixth support rod 9f are arranged along the diameter direction of the second annular frame 81b, and the fifth support rod 9e and the sixth support rod 9f are connected to each other by the main rotation shaft 3. And rotate with the main rotation axis 3. The seventh support rod 9g and the eighth support rod 9h are arranged along the diameter direction of the second holding ring 82b, and the seventh support rod 9g and the eighth support rod 9h are connected to each other by the main rotation shaft 3. And rotate with the main rotation axis 3.

第１の回転体２２ａの外周点は、図１４に示すように、第１の輪状フレーム８１ａあるいは第１の保持リング８２ａのいずれかの外周側の側面の任意の一点である。同様に、第２の回転体２２ｂの外周点は第２の輪状フレーム８１ｂあるいは第２の保持リング８２ｂのいずれかの外周側の側面の任意の一点となる。第１の回転体２２ａの外周点が描く外周円から定義される第１の回転面と、第２の回転体２２ｂの外周点が描く外周円から定義される第２の回転面とは、互いに平行に対向する関係である。   The outer peripheral point of the first rotary body 22a is, as shown in FIG. 14, an arbitrary point on the outer peripheral side of either the first annular frame 81a or the first holding ring 82a. Similarly, the outer peripheral point of the second rotating body 22b is an arbitrary one point on the outer peripheral side of either the second annular frame 81b or the second holding ring 82b. The first rotation surface defined by the outer circumference circle drawn by the outer peripheral point of the first rotation body 22a and the second rotation surface defined by the outer circumference circle drawn by the outer peripheral point of the second rotation body 22b mutually It is a relation facing in parallel.

第１の風受け羽根１１ａは、第１の支持棒９ａ及び第３の支持棒９ｃに上下を挟まれるように固定され、第２の風受け羽根１１ｂは、第２の支持棒９ｂ及び第４の支持棒９ｄに上下を挟まれるように固定されている。同様に、第３の風受け羽根１１ｃは、第５の支持棒９ｅ及び第７の支持棒９ｇに上下を挟まれるように固定され、第４の風受け羽根１１ｄは、第６の支持棒９ｆ及び第８の支持棒９ｈに上下を挟まれるように固定されている。   The first wind receiving blade 11a is fixed so as to be vertically sandwiched by the first support rod 9a and the third support rod 9c, and the second wind receiving blade 11b is formed of the second support rod 9b and the fourth support rod 9b. It is being fixed so that the upper and lower sides may be pinched | interposed to 9 d of support rods. Similarly, the third wind receiving blade 11c is fixed so as to be vertically sandwiched by the fifth support rod 9e and the seventh support rod 9g, and the fourth wind receiving blade 11d is a sixth support rod 9f. And the eighth support rod 9h so as to be vertically sandwiched.

図１３に示すように、円筒面をなす第１のベアリング５ａの外周面にＴ字型に直交するように第１の支持棒９ａ及び第２の支持棒９ｂが固定され、円筒面をなす第２のベアリング５ｂの外周面にＴ字型に直交するように第３の支持棒９ｃ及び第４の支持棒９ｄが固定されている。第１の支持棒９ａ、第２の支持棒９ｂ、第３の支持棒９ｃ、第４の支持棒９ｄは互いに同一形状であり、第１の支持棒９ａ及び第２の支持棒９ｂの長手方向は主回転軸３を挟んで互いに同一直線状に位置し、第３の支持棒９ｃ及び第４の支持棒９ｄの長手方向は主回転軸３を挟んで互いに同一直線状に位置する。第１の支持棒９ａの上面端部付近及び第３の支持棒９ｃの下面端部付近に第１の風受け羽根１１ａが固定され、第２の支持棒９ｂの上面端部付近及び第４の支持棒９ｄの下面端部付近に、第１の風受け羽根１１ａと同一形状の第２の風受け羽根１１ｂが、第１の風受け羽根１１ａとは風受け用の凹部を反対の向きになるように固定されている。第１の風受け羽根１１ａ及び第２の風受け羽根１１ｂの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第１の保持リング８２ａは、第１の支持棒９ａ及び第２の支持棒９ｂのそれぞれの外周側の端部に固定されている。第１の輪状フレーム８１ａは、上面に放射状の第１の駆動ギアの歯を有し、第３の支持棒９ｃ及び第４の支持棒９ｄのそれぞれの外周側の端部に固定されている。第１の保持リング８２ａ及び第１の輪状フレーム８１ａの中心には主回転軸３が位置する。第１の回転体２２ａは、風を受けると、第１のベアリング５ａ及び第２のベアリング５ｂごと第１方向に回転する。   As shown in FIG. 13, the first support rod 9 a and the second support rod 9 b are fixed to the outer peripheral surface of the first bearing 5 a forming a cylindrical surface so as to be orthogonal to the T shape, A third support rod 9c and a fourth support rod 9d are fixed to the outer peripheral surface of the second bearing 5b so as to be orthogonal to the T-shape. The first support bar 9a, the second support bar 9b, the third support bar 9c, and the fourth support bar 9d have the same shape, and the longitudinal direction of the first support bar 9a and the second support bar 9b. Are positioned on the same straight line with respect to the main rotation axis 3, and the longitudinal directions of the third support rod 9 c and the fourth support bar 9 d are positioned on the same straight line with respect to the main rotation axis 3. The first air receiving blade 11a is fixed in the vicinity of the upper surface end of the first support rod 9a and in the vicinity of the lower surface end of the third support rod 9c, and in the vicinity of the upper surface end of the second support rod 9b In the vicinity of the lower surface end of the support rod 9d, a second wind receiving blade 11b having the same shape as the first wind receiving blade 11a has a concave for wind receiving opposite to the first wind receiving blade 11a. As fixed. The fixed locations of the first wind receiving blade 11 a and the second wind receiving blade 11 b are in a symmetrical positional relationship with respect to the main rotation axis 3. The first holding ring 82a is fixed to the outer peripheral end of each of the first support rod 9a and the second support rod 9b. The first annular frame 81a has the radial first drive gear teeth on the top surface, and is fixed to the outer peripheral end of each of the third support rod 9c and the fourth support rod 9d. The main rotation shaft 3 is located at the center of the first holding ring 82a and the first annular frame 81a. When wind is received, the first rotating body 22a rotates in the first direction together with the first bearing 5a and the second bearing 5b.

図１３に示すように、主回転軸３の長手方向にＴ字型に直交するように第５〜第８の支持棒９ｅ〜９ｈが固定されている。第５〜第８の支持棒９ｅ〜９ｈは互いに同一形状であり、第５の支持棒９ｅ及び第６の支持棒９ｆの長手方向は主回転軸３を挟んで互いに同一直線状に位置し、第７の支持棒９ｇ及び第８の支持棒９ｈの長手方向は主回転軸３を挟んで互いに同一直線状に位置する。風を受けると第２の回転体２２ｂが第１の回転体２２ａと逆回転するような方向へ風受け用の凹部を向けて、第５の支持棒９ｅの上面端部付近及び第７の支持棒９ｇの下面端部付近に、第１の風受け羽根１１ａと同一形状の第３の風受け羽根１１ｃが固定され、第６の支持棒９ｆの上面端部付近及び第８の支持棒９ｈの下面端部付近に、第１の風受け羽根１１ａと同一形状の第４の風受け羽根１１ｄが、第３の風受け羽根１１ｃとは風受け用の凹部を反対の向きになるように固定されている。第３の風受け羽根１１ｃ及び第４の風受け羽根１１ｄの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第２の輪状フレーム８１ｂは、下面に放射状の第２の駆動ギアの歯を有し、第５の支持棒９ｅ及び第６の支持棒９ｆのそれぞれの外周側の端部に固定されている。第２の保持リング８２ｂは、第７の支持棒９ｇ及び第８の支持棒９ｈのそれぞれの外周側の端部に固定されている。第２の輪状フレーム８１ｂ及び第２の保持リング８２ｂの中心には主回転軸３が位置する。   As shown in FIG. 13, fifth to eighth support rods 9 e to 9 h are fixed so as to be orthogonal to the T-shape in the longitudinal direction of the main rotation shaft 3. The fifth to eighth support rods 9e to 9h have the same shape, and the longitudinal directions of the fifth support rod 9e and the sixth support rod 9f are located on the same straight line with respect to the main rotation shaft 3, The longitudinal directions of the seventh support rod 9g and the eighth support rod 9h are located on the same straight line with the main rotation axis 3 interposed therebetween. A concave portion for receiving the wind is directed in such a direction that the second rotary body 22b rotates in reverse with the first rotary body 22a when wind is received, and the vicinity of the upper surface end of the fifth support rod 9e and the seventh support A third wind receiving blade 11c having the same shape as the first wind receiving blade 11a is fixed in the vicinity of the lower surface end of the rod 9g, and in the vicinity of the upper surface end of the sixth support rod 9f and of the eighth support rod 9h. In the vicinity of the lower surface end, a fourth wind receiving blade 11d having the same shape as the first wind receiving blade 11a is fixed so that the recess for wind receiving is opposite to the third wind receiving blade 11c. ing. The fixing points of the third wind receiving blade 11 c and the fourth wind receiving blade 11 d are in a symmetrical positional relationship with the main rotation axis 3 interposed therebetween. The second annular frame 81b has radial second drive gear teeth on the lower surface, and is fixed to the outer peripheral end of each of the fifth support rod 9e and the sixth support rod 9f. The second holding ring 82b is fixed to the outer peripheral end of each of the seventh support rod 9g and the eighth support rod 9h. The main rotation shaft 3 is located at the center of the second annular frame 81 b and the second holding ring 82 b.

図１４に示すように、第１の動力ギア３１ａの歯は第１の輪状フレーム８１ａの第１の駆動ギアの歯及び第２の輪状フレーム８１ｂの第２の駆動ギアの歯に垂直にかみ合って回転するように設けられている。風を受けて第１の回転体２２ａ及び第２の回転体２２ｂが回転すると、それらの回転で第１の動力ギア３１ａは回転し、第１の動力ギア３１ａの回転は第１の動力ギア回転軸６１ａを介して、支柱７aに保持されている第１の発電機６２ａに伝達され、発電が行われる。第１の実施の形態に係る発電装置と同様、第１の動力ギア３１ａは、第１の回転体２２ａ及び第２の回転体２２ｂに挟まれ、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の動力ギア３１ａの回転力は大きくなる。第１の対向動力ギア３１ｂも第１の動力ギア３１ａと同様に、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の対向動力ギア３１ｂの回転力は大きくなる。   As shown in FIG. 14, the teeth of the first power gear 31a are vertically engaged with the teeth of the first drive gear of the first annular frame 81a and the teeth of the second drive gear of the second annular frame 81b. It is provided to rotate. When the first rotating body 22a and the second rotating body 22b rotate in response to the wind, the rotation of the first power gear 31a is rotated, and the rotation of the first power gear 31a is the rotation of the first power gear 31a. Power is transmitted to the first generator 62a held by the support 7a via the shaft 61a. As with the power generation device according to the first embodiment, the first power gear 31a is sandwiched between the first rotating body 22a and the second rotating body 22b, and obtains rotational torque from both rotating bodies. The rotational force of the first power gear 31a is larger than when there is only one rotating body. Similarly to the first power gear 31a, since the first opposing power gear 31b obtains rotational torque from both rotating bodies, the rotational force of the first opposing power gear 31b is greater than when only one rotating body is provided. Will grow.

一方の風受け羽根が受け流した風を受ける他方の風受け羽根の存在により、風が有効利用され、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂの回転トルクが大きくなることについても、第１の実施の形態に係る発電装置と同様である。   With regard to the fact that the wind is effectively used by the presence of the other wind receiving blade that receives the wind received by one of the wind receiving blades, and the rotational torque of the first power gear 31a and the first opposing power gear 31b is increased. It is the same as the power generation device according to the first embodiment.

図１５の拡大図に示すように、第１の動力ギア３１ａの歯は、第１の輪状フレーム８１ａ及び第２の輪状フレーム８１ｂの各駆動ギアの歯にかみ合っている。第１の輪状フレーム８１ａには第１の駆動ギアの歯７１ａ１、７１ａ２、・・・が第１の輪状フレーム８１ａと一体となる形で設けられ、第２の輪状フレーム８１ｂには第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・が第２の輪状フレーム８１ｂと一体となる形で設けられている。風を受けると、図１６の断面図に示す第１の輪状フレーム８１ａは図１６に向かって左方向、第２の輪状フレーム８１ｂは図１６に向かって右方向に動く。第１の動力ギア３１ａの歯と、第１の駆動ギアの歯７１ａ１、７１ａ２、・・・及び第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・はかみ合っているので、第１の輪状フレーム８１ａ及び第２の輪状フレーム８１ｂが動くに伴い、第１の動力ギア３１ａは第１の動力ギア回転軸６１ａを軸として図１６のＡ方向に回転する。第１の対向動力ギア３１ｂも同様の仕組みで回転する。 As shown in the enlarged view of FIG. 15, the teeth of the first power gear 31a mesh with the teeth of the drive gears of the first annular frame 81a and the second annular frame 81b. The first drive gear teeth 71a 1 , 71a 2 ,... Are provided integrally with the first ring-shaped frame 81a in the first ring-shaped frame 81a, and the second ring-shaped frame 81b is formed with the second ring-shaped frame 81b. The drive gear teeth 71b 1 , 71b 2 ,... Are provided integrally with the second annular frame 81b. When wind is received, the first annular frame 81a shown in the cross-sectional view of FIG. 16 moves leftward in FIG. 16 and the second annular frame 81b moves rightward in FIG. The teeth of the first power gear 31a, the teeth 71a 1 of the first driving gear, 71a 2, teeth 71b 1 ... and the second drive gear, 71b 2, since ... are engaged, the As the one annular frame 81a and the second annular frame 81b move, the first power gear 31a rotates about the first power gear rotary shaft 61a in the direction A in FIG. The first opposing power gear 31b also rotates in the same manner.

本発明の第２の実施の形態に係る発電装置では、図１７に示すように第１の回転体２２ａ及び第２の回転体２２ｂの各支持棒が互いに平行となっていない初期位置の場合でも、図１３に示す場合と同様に、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂが両回転体から回転トルクを得られることには変わりがないので、回転体が１つしかない場合に比べ、大きな回転力を得ることができる。   In the power generation apparatus according to the second embodiment of the present invention, as shown in FIG. 17, even when the support rods of the first rotating body 22a and the second rotating body 22b are not parallel to one another, Similarly to the case shown in FIG. 13, since there is no change in that the first power gear 31a and the first opposing power gear 31b can obtain rotational torque from both rotating bodies, there is only one rotating body. It is possible to obtain a large rotational force as compared with.

更に、図１７に示すように、風受け羽根の初期位置が、ある風受け羽根の受け流した風を他の風受け羽根が受けないような位置であっても、風を受けて上下の回転体が互いに逆回転し、ある風受け羽根が受け流した風を別の風受け羽根が受けるような位置になるのであれば、受け流した風が有効利用されることになり、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂは大きな回転トルクを得ることができる。   Furthermore, as shown in FIG. 17, even if the initial position of the wind receiving blade is a position where the wind received by one of the wind receiving blades is not received by the other wind receiving blades, the wind is received by the wind and the upper and lower rotating bodies Are in such a position that they rotate in reverse to each other such that wind received by one wind receiving blade is received by another wind receiving blade, the received wind is effectively used, and the first power gear 31 a and the first power gear 31 a The first opposing power gear 31 b can obtain a large rotational torque.

既に述べたとおり、風力の弱い低速回転では発電機の極数が多い方が有利であるが、極数が多くなると発電機の内部抵抗が増える。第２の実施の形態に係る発電装置によれば、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂは、第１の回転体２１ａ及び第２の回転体２１ｂの両方から回転トルクを得ることができるので、内部抵抗の大きな多極発電機を用いることによって、風力が弱い環境でも発電機の回転トルクを大きくすることができ、効率よく安定した発電をすることができる。   As described above, it is advantageous for the generator to have a large number of poles for low-speed rotation of the wind power, but an increase in the number of poles increases the internal resistance of the generator. According to the power generation apparatus of the second embodiment, the first power gear 31a and the first opposing power gear 31b obtain rotational torque from both the first rotating body 21a and the second rotating body 21b. Therefore, by using a multipole generator having a large internal resistance, the rotational torque of the generator can be increased even in an environment where wind power is weak, and efficient and stable power generation can be performed.

（第３の実施の形態）
発電装置の輪状フレームの駆動ギアは、輪状フレームの上面又は下面の表面にではなく、上面又は下面に設けられた溝の底に設けるタイプでもよい。図１８の正面図に示すように、本発明の第３の実施の形態に係る発電装置は、主回転軸３と、流体力（風力）により主回転軸３の周りを第１方向に回転する第１の回転体２３ａと、第１の回転体２３ａが定義する第１の回転面と平行に対向する第２の回転面を有し、第２の回転面が第１方向と反対の第２方向に、流体力（風力）により主回転軸３の周りを回転する第２の回転体２３ｂを備える。第３の実施の形態に係る発電装置は更に、第１の回転体２３ａ及び第２の回転体２３ｂの両者によって回転トルクが付与されて回転する第１の動力ギア３１ａと、第１の動力ギア３１ａの回転によって駆動される第１の発電機６２ａを備える。第１及び第２の回転面の定義は第１の実施の形態と同様である。 Third Embodiment
The drive gear of the ring-shaped frame of the power generator may be of the type not provided on the surface of the upper or lower surface of the ring-shaped frame but on the bottom of the groove provided on the upper or lower surface. As shown in the front view of FIG. 18, the power generation apparatus according to the third embodiment of the present invention rotates in the first direction around the main rotation shaft 3 by the main rotation shaft 3 and fluid force (wind force) A second rotating surface opposite to the first rotating surface defined by the first rotating body 23a and the first rotating surface defined by the first rotating body 23a, the second rotating surface being opposite to the first direction In the direction, the second rotating body 23 b is provided to rotate around the main rotation axis 3 by fluid force (wind force). The power generation apparatus according to the third embodiment further includes a first power gear 31a that is rotated by applying a rotational torque by both the first rotating body 23a and the second rotating body 23b, and a first power gear 31a. A first generator 62a driven by the rotation of 31a is provided. The definitions of the first and second rotation surfaces are the same as in the first embodiment.

図１８に示す本発明の第３の実施の形態に係る発電装置は、２つの輪状フレーム以外はすべて、図１３及び図１４に示す第２の実施の形態に係る発電装置と同様の構造を有する。図１８に示すように、第２の実施の形態に係る発電装置の第１の輪状フレーム８１ａ及び第２の輪状フレーム８１ｂの代わりに、第３の実施の形態に係る発電装置は第１の輪状フレーム８３ａ及び第２の輪状フレーム８３ｂを有している。   The power generation device according to the third embodiment of the present invention shown in FIG. 18 has the same structure as that of the power generation device according to the second embodiment shown in FIGS. 13 and 14 except for the two ring-shaped frames. . As shown in FIG. 18, instead of the first annular frame 81 a and the second annular frame 81 b of the power generation apparatus according to the second embodiment, the power generation apparatus according to the third embodiment has a first annular shape. It has a frame 83a and a second annular frame 83b.

図１９の拡大図に示すように、第１の動力ギア３１ａの歯は、第１の輪状フレーム８３ａ及び第２の輪状フレーム８３ｂのそれぞれにつけられた第１の溝９１ａ及び第２の溝９１ｂに垂直にはめ込まれるように設けられている。第１の溝９１ａ及び第２の溝９１ｂの底にはそれぞれ第１及び第２の駆動ギアが設けられ、第１及び第２の駆動ギアのそれぞれの歯と第１の動力ギア３１ａの歯がかみ合っているのである。第１の対向動力ギア３１ｂについても同様の構造である。図２０の断面図において、第１の輪状フレーム８３ａには第１の駆動ギアの歯７１ａ１、７１ａ２、・・・が設けられ、第２の輪状フレーム８３ｂには第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・が設けられている。風を受けると、図２０の断面図に示す第１の輪状フレーム８３ａは図２０に向かって左方向、第２の輪状フレーム８３ｂは図２０に向かって右方向に動く。第１の動力ギア３１ａの歯と、第１の駆動ギアの歯７１ａ１、７１ａ２、・・・及び第２の駆動ギアの歯７１ｂ１、７１ｂ２、・・・はかみ合っているので、第１の輪状フレーム８３ａ及び第２の輪状フレーム８３ｂが動くに伴い、第１の動力ギア３１ａは第１の動力ギア回転軸６１ａを軸としてＡ方向に回転する。第１の対向動力ギア３１ｂについても同様である。 As shown in the enlarged view of FIG. 19, the teeth of the first power gear 31a are in the first groove 91a and the second groove 91b provided in the first annular frame 83a and the second annular frame 83b, respectively. It is provided to be fitted vertically. First and second drive gears are provided at the bottom of the first groove 91a and the second groove 91b, respectively, and the teeth of the first and second drive gears and the teeth of the first power gear 31a are It is engaged. The same structure is applied to the first opposing power gear 31b. In the sectional view of FIG. 20, the first ring-shaped frame 83a is provided with the teeth 71a 1 , 71a 2 ... Of the first drive gear, and the second ring-shaped frame 83b is provided with the teeth of the second drive gear. 71b 1 , 71b 2 ,... Are provided. When wind is received, the first annular frame 83a shown in the cross-sectional view of FIG. 20 moves to the left in FIG. 20, and the second annular frame 83b moves to the right in FIG. The teeth of the first power gear 31a, the teeth 71a 1 of the first driving gear, 71a 2, teeth 71b 1 ... and the second drive gear, 71b 2, since ... are engaged, the As the first ring-shaped frame 83a and the second ring-shaped frame 83b move, the first power gear 31a rotates in the A direction about the first power gear rotary shaft 61a. The same applies to the first opposing power gear 31b.

図２１の上面図に示すように、第１の輪状フレーム８３ａには、上面の外周付近に一定の深さで第１の輪状フレーム８３ａの外周と同心円状で一定の幅の第１の溝９１ａが設けられている。第２の輪状フレーム８３ｂと第２の溝９１ｂとの関係についても同様である。   As shown in the top view of FIG. 21, in the first annular frame 83a, the first groove 91a having a constant width concentric with the outer periphery of the first annular frame 83a at a constant depth near the outer periphery of the upper surface Is provided. The same applies to the relationship between the second annular frame 83b and the second groove 91b.

第１の実施の形態に係る発電装置と同様、第３の実施の形態に係る発電装置の第１の動力ギア３１ａは、第１の回転体２３ａ及び第２の回転体２３ｂに挟まれ、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の動力ギア３１ａの回転力は大きくなる。第１の対向動力ギア３１ｂについても同様である。   Similar to the power generation device according to the first embodiment, the first power gear 31a of the power generation device according to the third embodiment is sandwiched between the first rotating body 23a and the second rotating body 23b, Since rotational torque is obtained from the rotating body, the rotational force of the first power gear 31a is larger than in the case where there is only one rotating body. The same applies to the first opposing power gear 31b.

一方の風受け羽根が受け流した風を受ける他方の風受け羽根の存在により、風が有効利用され、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂの回転トルクが大きくなることについても、第１の実施の形態に係る発電装置と同様である。よって、第３の実施の形態に係る発電装置によれば、発電機の回転トルクを大きくすることができるので、内部抵抗の大きな多極発電機を用いることにより、風力が弱い環境でも効率よく安定した発電をすることができる。   With regard to the fact that the wind is effectively used by the presence of the other wind receiving blade that receives the wind received by one of the wind receiving blades, and the rotational torque of the first power gear 31a and the first opposing power gear 31b is increased. It is the same as the power generation device according to the first embodiment. Therefore, according to the power generation apparatus according to the third embodiment, the rotational torque of the generator can be increased, and therefore, by using the multipole generator having a large internal resistance, it is efficiently stabilized even in an environment where wind power is weak. Can generate electricity.

（第４の実施の形態）
発電装置の各回転体の間には、回転体自身の重量を分散するための重量支持器を設けることも可能である。図２２の正面図に示すように、本発明の第４の実施の形態に係る発電装置は、主回転軸３と、流体力（風力）により主回転軸３の周りを第１方向に回転する第１の回転体２２ａと、第１の回転体２２ａが定義する第１の回転面と平行に対向する第２の回転面を有し、第２の回転面が第１方向と反対の第２方向に、流体力（風力）により主回転軸３の周りを回転する第２の回転体２２ｂを備える。第４の実施の形態に係る発電装置は更に、第１の回転体２２ａ及び第２の回転体２２ｂの両者によって回転トルクが付与されて回転する第１の動力ギア３１ａと、第１の動力ギア３１ａの回転によって駆動される第１の発電機６２ａを備える。第１及び第２の回転面の定義は第１の実施の形態と同様である。 Fourth Embodiment
It is also possible to provide a weight support for distributing the weight of the rotating body itself between the rotating bodies of the power generation device. As shown in the front view of FIG. 22, the power generation device according to the fourth embodiment of the present invention rotates in the first direction around the main rotation shaft 3 by the main rotation shaft 3 and fluid force (wind force) A second rotating surface opposite to the first rotating surface defined by the first rotating body 22a and the first rotating surface defined by the first rotating body 22a, the second rotating surface being opposite to the first direction In the direction, the second rotating body 22 b is provided to rotate around the main rotation axis 3 by fluid force (wind force). The power generation apparatus according to the fourth embodiment further includes a first power gear 31a that is rotated by applying a rotational torque by both the first rotating body 22a and the second rotating body 22b, and a first power gear 31a. A first generator 62a driven by the rotation of 31a is provided. The definitions of the first and second rotation surfaces are the same as in the first embodiment.

図２２に示すように、本発明の第４の実施の形態に係る発電装置は、図１３及び図１４に示す本発明の第２の実施の形態に係る発電装置と同様の構造に加え、重量支持器とその重量支持器がはめこまれている重量支持器用レールを更に備える。   As shown in FIG. 22, the power generation apparatus according to the fourth embodiment of the present invention has a weight in addition to the structure similar to that of the power generation apparatus according to the second embodiment of the present invention shown in FIGS. It further comprises a weight support rail on which the support and its weight support are fitted.

重量支持器は、重量支持器用タイヤ、重量支持器用タイヤの回転軸、重量支持器用土台（外側）及び重量支持器用土台（内側）からなる。図２２に示すように、第１の重量支持器用タイヤ１０１ａは、第１の重量支持器用土台（外側）１０３ａ１及び第１の重量支持器用土台（内側）１０３ａ２に渡された回転軸にはめ込まれ、この回転軸を中心に回転する。第２〜第４の重量支持器用タイヤ１０１ｂ〜１０１ｄでも同様である。第１の重量支持器用土台（外側）１０３ａ１及び第１の重量支持器用土台（内側）１０３ａ２は、図示は省略するが、第３の支持棒９ｃの上面に固定されている。第２の重量支持器用土台（外側）１０３ｂ１及び第２の重量支持器用土台（内側）１０３ｂ２も同様である。第３の重量支持器用土台（外側）１０３ｃ１及び第３の重量支持器用土台（内側）１０３ｃ２は、図示は省略するが、第４の支持棒９ｄの上面に固定されている。第４の重量支持器用土台（外側）１０３ｄ１及び第４の重量支持器用土台（内側）１０３ｄ２も同様である。第１の重量支持器用レール９３ａは、図示は省略するが、第２の重量支持器用タイヤ１０１ｂ及び第３の重量支持器用タイヤ１０１ｃがはめ込まれて転がることができるような凹みを有する、主回転軸３を中心とした輪状構造であり、第５の支持棒９ｅ及び第６の支持棒９ｆの下面に固定されている。第２の重量支持器用レール９３ｂも同様であるが、第１の重量支持器用タイヤ１０１ａ及び第４の重量支持器用タイヤ１０１ｄがはめ込まれて転がることができるような凹みを有し、第１の重量支持器用レール９３ａの外側に位置する。第１の重量支持器用タイヤ１０１ａ及び第４の重量支持器用タイヤ１０１ｄは第２の重量支持器用レール９３ｂに接し、第２の重量支持器用タイヤ１０１ｂ及び第３の重量支持器用タイヤ１０１ｃは第１の重量支持器用レール９３ａに接する。 The weight support device comprises a weight support device tire, a rotation shaft of the weight support device tire, a weight support device base (outside) and a weight support device base (inner side). As shown in FIG. 22, the first weight carrier tire 101a is fitted to the first weight carrier base (outside) 103a 1 and the first weight carrier base (inner) 103a 2 at the rotation shaft. And rotate around this rotation axis. The same applies to the second to fourth weight support device tires 101b to 101d. The first weight bearing dexterity foundation (outer) 103a 1 and the first weight bearing dexterity base (inner) 103a 2 is not shown, is fixed to the upper surface of the third support rod 9c. The same applies to the second weight support base (outside) 103b 1 and the second weight support base (inner) 103b 2 . The third weight bearing dexterity foundation (outer) 103c 1 and the third weight bearing dexterity base (inner) 103c 2 are not shown, are fixed to the upper surface of the fourth support rod 9d. The same applies to the fourth weight support base (outside) 103d 1 and the fourth weight support base (inner) 103d 2 . Although not shown, the first weight carrier rail 93a has a recess that allows the second weight carrier tire 101b and the third weight carrier tire 101c to be fitted and rolled. The ring-shaped structure centering on 3 is fixed to the lower surface of the fifth support rod 9e and the sixth support rod 9f. The second weight support device rail 93b is also similar, but has a recess that allows the first weight support device tire 101a and the fourth weight support device tire 101d to be fitted and rolled, and the first weight It is located outside the support rail 93a. The first weight support device tire 101a and the fourth weight support device tire 101d are in contact with the second weight support device rail 93b, and the second weight support device tire 101b and the third weight support device tire 101c are the first. Contact the weight support rail 93a.

風を受けて第１の回転体２２ａ及び第２の回転体２２ｂが互いに逆回転する際は、第１〜第４の重量支持器用タイヤ１０１ａ〜１０１ｄは、第１の重量支持器用レール９３ａ及び第２の重量支持器用レール９３ｂを介して第２の回転体２２ｂの重量の一部を負担しながら、第１の重量支持器用レール９３ａ及び第２の重量支持器用レール９３ｂに沿って転がる。これらの重量支持器がない場合は、第２の回転体２２ｂの重量は、主回転軸３と第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂにかかることになる。重量支持器がある場合は、第１〜第４の重量支持器用タイヤ１０１ａ〜１０１ｄの部分でも第２の回転体２２ｂの重量受けることになり、第２の回転体２２ｂの重量は分散する。それにより、第２の回転体２２ｂの第５〜第８の支持棒９ｅ〜９ｈが下方にたわんでしまうことや、重量がかかりすぎるために第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂが回転しなくなること等を防ぐことができる。重量支持器及び重量支持器用レールの個数は、回転体の重量によって増減することができる。   When the first rotating body 22a and the second rotating body 22b reversely rotate relative to each other in response to wind, the first to fourth weight support device tires 101a to 101d are the first weight support device rails 93a and the first weight support device rails While bearing a part of the weight of the second rotating body 22b via the second weight support rail 93b, the second weight support rail 93b rolls along the first weight support rail 93a and the second weight support rail 93b. If these weight support devices are not provided, the weight of the second rotating body 22b is applied to the main rotation shaft 3, the first power gear 31a, and the first opposing power gear 31b. When there is a weight support, the weight of the second rotation body 22b is also received by the weight of the second rotation body 22b even in the portions of the first to fourth weight support device tires 101a to 101d. As a result, the fifth to eighth support rods 9e to 9h of the second rotating body 22b may be bent downward, or the first power gear 31a and the first opposing power gear 31b may be too heavy. Can be prevented from rotating. The number of weight carriers and weight carrier rails can be increased or decreased depending on the weight of the rotating body.

第１の実施の形態に係る発電装置と同様、第１の動力ギア３１ａは、第１の回転体２２ａ及び第２の回転体２２ｂに挟まれ、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の動力ギア３１ａの回転力は大きくなる。第１の対向動力ギア３１ｂについても同様である。   As with the power generation device according to the first embodiment, the first power gear 31a is sandwiched between the first rotating body 22a and the second rotating body 22b, and obtains rotational torque from both rotating bodies. The rotational force of the first power gear 31a is larger than when there is only one rotating body. The same applies to the first opposing power gear 31b.

一方の風受け羽根が受け流した風を受ける他方の風受け羽根の存在により、風が有効利用され、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂの回転トルクが大きくなることについても、第１の実施の形態に係る発電装置と同様である。よって、第４の実施の形態に係る発電装置によれば、内部抵抗の大きな多極発電機を用いることにより、風力が弱い環境でも効率よく安定した発電をすることができる。   With regard to the fact that the wind is effectively used by the presence of the other wind receiving blade that receives the wind received by one of the wind receiving blades, and the rotational torque of the first power gear 31a and the first opposing power gear 31b is increased. It is the same as the power generation device according to the first embodiment. Therefore, according to the power generation device according to the fourth embodiment, by using the multipole generator having a large internal resistance, efficient and stable power generation can be performed even in an environment where wind power is weak.

（第５の実施の形態）
発電装置の動力ギアは、第１の駆動ギア及び第２の駆動ギア等の設けられた輪状フレームを用いずとも、風受け羽根の接触で直接回転させることも可能である。図２３の斜視図に示すように、本発明の第５の実施の形態に係る発電装置は、主回転軸３と、流体力（風力）により主回転軸３の周りを第１方向（図２３のＢ方向）に回転する第１の回転体２４ａと、第１の回転体２４ａが定義する第１の回転面と平行に対向する第２の回転面を有し、第２の回転面が第１方向と反対の第２方向（図２３のＡ方向）に、流体力（風力）により主回転軸３の周りを回転する第２の回転体２４ｂを備える。第５の実施の形態に係る発電装置は更に、第１の回転体２４ａ及び第２の回転体２４ｂの両者によって回転トルクが付与されて回転する第１の動力ギア３１ａと、第１の動力ギア３１ａの回転によって駆動される第１の発電機６２ａを備える。第１及び第２の回転面の定義は第１の実施の形態と同様である。 Fifth Embodiment
The power gear of the power generation device can also be directly rotated by the contact of the wind receiving blade without using an annular frame provided with the first drive gear, the second drive gear and the like. As shown in the perspective view of FIG. 23, the power generation apparatus according to the fifth embodiment of the present invention has a main rotating shaft 3 and a first direction (FIG. 23) around the main rotating shaft 3 by fluid force (wind force). The first rotary body 24a that rotates in the direction B) and the second rotary surface facing in parallel with the first rotary surface defined by the first rotary body 24a, the second rotary surface being the first A second rotating body 24b is provided which rotates around the main rotation axis 3 by fluid force (wind force) in a second direction (direction A in FIG. 23) opposite to one direction. The power generation apparatus according to the fifth embodiment further includes a first power gear 31a that is rotated by applying a rotational torque by both the first rotating body 24a and the second rotating body 24b, and a first power gear 31a. A first generator 62a driven by the rotation of 31a is provided. The definitions of the first and second rotation surfaces are the same as in the first embodiment.

図２３の斜視図に示すように、主回転軸３は土台１に据え付けられ、重力方向に直立し、第２方向（図２３のＡ方向）に回転する。土台１の内部には、主回転軸３の回転エネルギーを取り出すための発電機が設置されていてもよい。   As shown in the perspective view of FIG. 23, the main rotation shaft 3 is mounted on the base 1, stands upright in the direction of gravity, and rotates in the second direction (direction A in FIG. 23). A generator for extracting rotational energy of the main rotation shaft 3 may be installed inside the base 1.

図２３に示すように、円筒面をなすベアリング５ａの外周面には、Ｔ字型に直交するように第１の支持棒９ａ及び第２の支持棒９ｂが固定されている。第１の支持棒９ａ及び第２の支持棒９ｂは互いに同一形状であり、長手方向は主回転軸３を挟んで互いに同一直線状に位置する。第１の支持棒９ａの外周側の端部に第１の風受け羽根１１ａが固定され、第２の支持棒９ｂの外周側の端部に第１の風受け羽根１１ａと同一形状の第２の風受け羽根１１ｂが、第１の風受け羽根１１ａとは風受け用の凹部を反対の向きになるように固定されている。第１の風受け羽根１１ａ及び第２の風受け羽根１１ｂの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第１の回転体２４ａは、風を受けると、ベアリング５ａごと第１方向（図２３のＢ方向）に回転する。   As shown in FIG. 23, a first support rod 9a and a second support rod 9b are fixed to the outer peripheral surface of the cylindrical bearing 5a so as to be orthogonal to the T-shape. The first support rods 9a and the second support rods 9b have the same shape, and the longitudinal directions are located on the same straight line with the main rotation shaft 3 interposed therebetween. The first wind receiving blade 11a is fixed to the outer circumferential end of the first support rod 9a, and the second wind bearing 11a has the same shape as the first wind receiving blade 11a at the outer circumferential end of the second support rod 9b. The wind receiving blade 11b is fixed so that the recess for receiving the wind is opposite to the first wind receiving blade 11a. The fixed locations of the first wind receiving blade 11 a and the second wind receiving blade 11 b are in a symmetrical positional relationship with respect to the main rotation axis 3. When receiving the wind, the first rotating body 24a rotates in the first direction (direction B in FIG. 23) together with the bearing 5a.

図２３に示すように、第２の回転体２４ｂにおいて、主回転軸３の長手方向にＴ字型に直交するように第３の支持棒９ｃ及び第４の支持棒９ｄが固定されている。第３の支持棒９ｃ及び第４の支持棒９ｄは互いに同一形状であり、長手方向は主回転軸３を挟んで互いに同一直線状に位置する。第３の支持棒９ｃ及び第４の支持棒９ｄは第１の回転体２４ａの上方に位置する。第３の支持棒９ｃの外周側の端部に、第２の回転体２４ｂが第１の回転体２４ａと逆回転するような方向へ風受け用の凹部を向けて、第１の風受け羽根１１ａと同一形状の第３の風受け羽根１１ｃが固定されている。第４の支持棒９ｄの外周側の端部に、第３の風受け羽根１１ｃとは風受け用の凹部を反対の向きになるように、第１の風受け羽根１１ａと同一形状の第４の風受け羽根１１ｄが固定されている。第３の風受け羽根１１ｃ及び第４の風受け羽根１１ｄの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第２の回転体２４ｂは、風を受けると第２方向（図２３のＡ方向）に回転する。   As shown in FIG. 23, in the second rotary body 24b, a third support rod 9c and a fourth support rod 9d are fixed so as to be orthogonal to the T-shape in the longitudinal direction of the main rotation shaft 3. The third support rod 9c and the fourth support rod 9d have the same shape, and the longitudinal directions are located on the same straight line with the main rotation shaft 3 interposed therebetween. The third support rod 9c and the fourth support rod 9d are located above the first rotating body 24a. At the end on the outer peripheral side of the third support rod 9c, the concave for wind reception is directed in such a direction that the second rotary body 24b rotates in the reverse direction to the first rotary body 24a. A third wind receiving blade 11c having the same shape as 11a is fixed. A fourth support rod 9d has an end on the outer circumferential side, and the fourth wind-receiving blade 11a has the same shape as the first wind-receiving blade 11a so that the recess for receiving the wind is opposite to the third wind-receiving blade 11c. The wind receiving blade 11d is fixed. The fixing points of the third wind receiving blade 11 c and the fourth wind receiving blade 11 d are in a symmetrical positional relationship with the main rotation axis 3 interposed therebetween. The second rotating body 24b rotates in a second direction (direction A in FIG. 23) when the wind is received.

第１の回転体２４ａの外周点は、図２３に示すように、第１の風受け羽根１１ａあるいは第２の風受け羽根１１ｂのいずれかの外周側の三角形型の側面のいずれかの頂点である。同様に、第２の回転体２４ｂの外周点は、第３の風受け羽根１１ｃあるいは第４の風受け羽根１１ｄのいずれかの外周側の三角形型の側面のいずれかの頂点となる。第１の回転体２４ａの外周点が描く外周円から定義される第１の回転面と、第２の回転体２４ｂの外周点が描く外周円から定義される第２の回転面とは、互いに平行に対向する関係である。   The outer peripheral point of the first rotating body 24a is, as shown in FIG. 23, an apex of one of the side faces of the triangular shape on the outer peripheral side of either the first wind receiving blade 11a or the second wind receiving blade 11b. is there. Similarly, the outer peripheral point of the second rotating body 24b is the apex of one of the side faces of the triangular shape on the outer peripheral side of either the third air receiving blade 11c or the fourth air receiving blade 11d. The first rotation surface defined by the outer circumference circle drawn by the outer circumference point of the first rotation body 24a and the second rotation plane defined by the outer circumference circle drawn by the outer circumference point of the second rotation body 24b mutually It is a relation facing in parallel.

図２３に示すように、第１の動力ギア３１ａの歯及び第１の対向動力ギア３１ｂの歯は、第１の風受け羽根１１ａの上部又は第２の風受け羽根１１ｂの上部と、第３の風受け羽根１１ｃの下部又は第４の風受け羽根１１ｄの下部に接触して回転する位置に設置されている。図２５の拡大断面図に示すように、風を受けると、第１の風受け羽根１１ａは図２５に向かって左方向、第３の風受け羽根１１ｃは図２５に向かって右方向に動く。第１の風受け羽根１１ａ及び第３の風受け羽根１１ｃが動くに伴い、第１の動力ギア３１ａは第１の動力ギア回転軸６１ａを軸としてＡ方向に回転する。図２３の第１の対向動力ギア３１ｂも、第１の動力ギア３１ａと同様のしくみで回転する。第１の実施の形態に係る発電装置と同様、第１の動力ギア３１ａは、第１の回転体２４ａ及び第２の回転体２４ｂにより、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の動力ギア３１ａの回転力は大きくなる。第１の対向動力ギア３１ｂについても同様である。図２５に示す第１の動力ギア３１ａの歯数は４であるが、風受け羽根と接触して回転するタイプであれば、歯数の増減は自由にすることができる。第１の対向動力ギア３１ｂについても同様である。   As shown in FIG. 23, the teeth of the first power gear 31a and the teeth of the first opposing power gear 31b are the upper portion of the first wind receiving blade 11a or the upper portion of the second wind receiving blade 11b, and the third It is installed in the position which contacts and rotates the lower part of the wind receiving blade 11c or the lower part of the 4th wind receiving blade 11d. As shown in the enlarged cross-sectional view of FIG. 25, when wind is received, the first wind receiving blade 11a moves to the left in FIG. 25, and the third wind receiving blade 11c moves to the right in FIG. As the first wind receiving blade 11a and the third wind receiving blade 11c move, the first power gear 31a rotates in the A direction about the first power gear rotation shaft 61a. The first opposing power gear 31 b of FIG. 23 also rotates in the same manner as the first power gear 31 a. As in the power generation apparatus according to the first embodiment, since the first power gear 31a obtains rotational torque from both rotating bodies by the first rotating body 24a and the second rotating body 24b, 1 The rotational force of the first power gear 31a is larger than when there are only two rotating bodies. The same applies to the first opposing power gear 31b. Although the number of teeth of the first power gear 31a shown in FIG. 25 is four, the number of teeth can be freely increased or decreased if it is of a type that rotates in contact with the wind receiving blade. The same applies to the first opposing power gear 31b.

一方の風受け羽根が受け流した風を受ける他方の風受け羽根の存在により、風が有効利用され、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂの回転トルクが大きくなることについても、第１の実施の形態に係る発電装置と同様である。よって、第５の実施の形態に係る発電装置によれば、内部抵抗の大きな多極発電機を用いることにより、風力が弱い環境でも効率よく安定した発電をすることができる。   With regard to the fact that the wind is effectively used by the presence of the other wind receiving blade that receives the wind received by one of the wind receiving blades, and the rotational torque of the first power gear 31a and the first opposing power gear 31b is increased. It is the same as the power generation device according to the first embodiment. Therefore, according to the power generation device according to the fifth embodiment, by using the multipole generator having a large internal resistance, efficient and stable power generation can be performed even in an environment where wind power is weak.

＜第５の実施の形態の変形例＞
図２６に示すように、本発明の第５の実施の形態の変形例に係る発電装置は、図２３に示す第１の回転体２４ａ及び第２の回転体２４ｂに、支持棒と風受け羽根のセットを２セットずつ増設したような多羽根型構造である。本発明の第５の実施の形態の変形例に係る発電装置は、主回転軸３と、流体力（風力）により主回転軸３の周りに第１方向に回転する第１の回転体と、第１の回転体が定義する第１の回転面と平行に対向する第２の回転面を有し、第２の回転面が第１方向と反対の第２方向に、流体力（風力）により主回転軸３の周りに回転する第２の回転体を備える。第５の実施の形態の変形例に係る発電装置は更に、第１の回転体及び第２の回転体の両者によって回転トルクが付与されて回転する第１の動力ギア３１ａと、第１の動力ギア３１ａの回転によって駆動される第１の発電機６２ａを備える。第１及び第２の回転面の定義は第１の実施の形態と同様である。 <Modification of Fifth Embodiment>
As shown in FIG. 26, in the power generation apparatus according to the modification of the fifth embodiment of the present invention, the supporting rod and the wind receiving blade are provided on the first rotating body 24a and the second rotating body 24b shown in FIG. It is a multi-vane type structure in which 2 sets of 2 sets are added. A power generation apparatus according to a modification of the fifth embodiment of the present invention includes: a main rotation shaft 3; and a first rotation body rotating in a first direction around the main rotation shaft 3 by fluid force (wind force); The first rotating body has a second rotation surface facing in parallel with the first rotation surface defined, the second rotation surface being in a second direction opposite to the first direction by a fluid force (wind force) A second rotating body that rotates around the main rotation axis 3 is provided. The power generation apparatus according to the modification of the fifth embodiment further includes: a first power gear 31a that is rotated by applying a rotational torque by both of the first and second rotating bodies; The first generator 62a is driven by the rotation of the gear 31a. The definitions of the first and second rotation surfaces are the same as in the first embodiment.

図２６の斜視図に示すように、主回転軸３は土台１に据え付けられ、重力方向に直立し、第２方向に回転する。土台１の内部には、主回転軸３の回転エネルギーを取り出すための発電機が設置されていてもよい。   As shown in the perspective view of FIG. 26, the main rotary shaft 3 is mounted on the base 1, stands upright in the direction of gravity, and rotates in the second direction. A generator for extracting rotational energy of the main rotation shaft 3 may be installed inside the base 1.

図２６に示すように、円筒面をなすベアリング５ａの外周面には、上側から見たときに主回転軸３に十字型に直交するように第１〜第４の支持棒９ａ〜９ｄが固定されている。第１〜第４の支持棒９ａ〜９ｄは互いに同一形状である。第１の支持棒９ａの外周側の端部に第１の風受け羽根１１ａが固定され、第２の支持棒９ｂの外周側の端部に第２の風受け羽根１１ｂが固定され、第３の支持棒９ｃの外周側の端部に第３の風受け羽根１１ｃが固定され、第４の支持棒９ｄの外周側の端部に第４の風受け羽根１１ｄが固定されている。第１〜第４の風受け羽根１１ａ〜１１ｄの形状は互いに同一であり、各風受け用の凹部は、風を受けた時に第１の回転体が第１方向に回転するように向けられている。第１の回転体は、風を受けるとベアリング５ａごと回転する。   As shown in FIG. 26, first to fourth support rods 9a to 9d are fixed on the outer peripheral surface of the cylindrical bearing 5a so as to be orthogonal to the main rotary shaft 3 when viewed from the upper side. It is done. The first to fourth support rods 9a to 9d have the same shape. The first air receiving blade 11a is fixed to the outer peripheral end of the first support rod 9a, and the second air receiving blade 11b is fixed to the outer peripheral end of the second support rod 9b. The third wind receiving blade 11c is fixed to the outer peripheral end of the support rod 9c, and the fourth wind receiving lid 11d is fixed to the outer peripheral end of the fourth support rod 9d. The shapes of the first to fourth wind receiving blades 11a to 11d are identical to each other, and the concave portions for each wind receiving are directed such that the first rotating body rotates in the first direction when the wind is received. There is. The first rotating body, together with the wind, rotates with the bearing 5a.

図２６に示すように、第２の回転体において、上側から見たときに主回転軸３に十字型に直交するように、第５〜第８の支持棒９ｅ〜９ｈが固定されている。第５〜第８の支持棒９ｅ〜９ｈは互いに同一形状である。第５の支持棒９ｅの外周側の端部に第５の風受け羽根１１ｅが固定され、第６の支持棒９ｆの外周側の端部に第６の風受け羽根１１ｆが固定され、第７の支持棒９ｇの外周側の端部に第７の風受け羽根１１ｇが固定され、第８の支持棒９ｈの外周側の端部に第８の風受け羽根１１ｈが固定されている。第５〜第８の風受け羽根１１ｅ〜１１ｈの形状は互いに同一であり、各風受け用の凹部は、風を受けた時に第２の回転体が第２方向に回転するように向けられている。第２の回転体は、風を受けると主回転軸３の周りを第１方向とは反対の第２方向に回転する。   As shown in FIG. 26, in the second rotating body, fifth to eighth support rods 9e to 9h are fixed so as to be orthogonal to the main rotary shaft 3 in a cruciform shape when viewed from the upper side. The fifth to eighth support rods 9e to 9h have the same shape. A fifth wind receiving blade 11e is fixed to the outer peripheral end of the fifth support rod 9e, and a sixth wind receiving blade 11f is fixed to the outer peripheral end of the sixth support rod 9f. A seventh air receiving blade 11g is fixed to the outer circumferential end of the support rod 9g, and an eighth wind receiving blade 11h is fixed to the outer circumferential end of the eighth support rod 9h. The shapes of the fifth to eighth wind receiving blades 11e to 11h are identical to each other, and the recess for each wind receiving is directed such that the second rotating body rotates in the second direction when the wind is received. There is. The second rotating body rotates around the main rotation axis 3 in a second direction opposite to the first direction when receiving the wind.

第１の回転体の外周点は、図２６に示すように、第１〜第４の風受け羽根１１ａ〜１１ｄのいずれかの外周側の三角形型の側面のいずれかの頂点である。同様に、第２の回転体の外周点は、第５〜第８の風受け羽根１１ｅ〜１１ｈのいずれかの外周側の三角形型の側面のいずれかの頂点となる。第１の回転体の外周点が描く外周円から定義される第１の回転面と、第２の回転体の外周点が描く外周円から定義される第２の回転面とは、互いに平行に対向する関係である。   The outer peripheral point of the first rotating body is, as shown in FIG. 26, an apex of any one of the outer peripheral side triangular side faces of the first to fourth wind receiving blades 11a to 11d. Similarly, the outer peripheral point of the second rotating body is an apex of any one of the fifth to eighth wind receiving blades 11e to 11h on the outer peripheral side of the triangular shape. The first rotation surface defined by the outer circumference circle drawn by the outer circumference point of the first rotation body and the second rotation plane defined by the outer circumference circle drawn by the outer circumference point of the second rotation body are mutually parallel It is an opposing relationship.

図２６に示すように、第１の動力ギア３１ａ、第１の対向動力ギア３１ｂ、第２の動力ギア３１ｃ、第２の対向動力ギア３１ｄのそれぞれの歯は、第１〜第４の風受け羽根１１ａ〜１１ｄのそれぞれの上部と、第５〜第８の風受け羽根１１ｅ〜１１ｈのそれぞれの下部に接触して回転する位置に設置されている。第１の動力ギア３１ａ、第１の対向動力ギア３１ｂ、第２の動力ギア３１ｃ、第２の対向動力ギア３１ｄは、本発明の第５の実施の形態に係る発電装置と同様の仕組みで回転し、それぞれ第１の動力ギア回転軸６１ａ、第１の対向動力ギア回転軸６１ｂ、第２の動力ギア回転軸６１ｃ、第２の対向動力ギア回転軸６１ｄを介して、支柱７aに保持されている第１の発電機６２ａ、支柱７ｂに保持されている第１の対向発電機６２ｂ、支柱７ｃに保持されている第２の発電機６２ｃ、支柱７ｄに保持されている第２の対向発電機６２ｄに回転が伝達され、発電される。第１の実施の形態に係る発電装置と同様、第１の動力ギア３１ａは、第１の回転体及び第２の回転体により、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の動力ギア３１ａの回転力は大きくなる。第１の対向動力ギア３１ｂ、第２の動力ギア３１ｃ、第２の対向動力ギア３１ｄについても同様である。なお、第１の発電機６２ａ、第２の発電機６２ｃを駆動する回転トルクの向上のためには、第１の対向発電機６２ｂ、第２の対向発電機６２ｄは無くてもよいことは既に述べたとおりである。   As shown in FIG. 26, the respective teeth of the first power gear 31a, the first opposing power gear 31b, the second power gear 31c, and the second opposing power gear 31d are the first to fourth wind receivers. It is installed in the position which contacts and rotates each upper part of blade | wing 11a-11d, and each lower part of 5th-8th wind receiving blade 11e-11h. The first power gear 31a, the first opposing power gear 31b, the second power gear 31c, and the second opposing power gear 31d rotate in the same manner as the generator according to the fifth embodiment of the present invention. Are held by the column 7a via the first power gear rotary shaft 61a, the first opposing power gear rotary shaft 61b, the second power gear rotary shaft 61c, and the second opposing power gear rotary shaft 61d, respectively. The first generator 62a, the first opposed generator 62b held by the support 7b, the second generator 62c held by the support 7c, and the second opposed generator held by the support 7d The rotation is transmitted to 62 d and generated. As in the power generation apparatus according to the first embodiment, the first power gear 31a obtains rotational torque from both rotating bodies by the first rotating body and the second rotating body, so that one rotation is achieved. The rotational force of the first power gear 31a is greater than when there is only a body. The same applies to the first opposing power gear 31b, the second power gear 31c, and the second opposing power gear 31d. In addition, in order to improve the rotational torque for driving the first generator 62a and the second generator 62c, the first opposing generator 62b and the second opposing generator 62d may already be omitted. As I said.

一方の風受け羽根が受け流した風を受ける他方の風受け羽根の存在により、風が有効利用され、第１の動力ギア３１ａ、第１の対向動力ギア３１ｂ、第２の動力ギア３１ｃ、第２の対向動力ギア３１ｄの回転トルクが大きくなることについても、第１〜第５の実施の形態に係る発電装置と同様である。このため、第５の実施の形態の変形例に係る発電装置によっても、内部抵抗の大きな多極発電機を有効利用することが可能になり、風力が弱い環境でも効率よく安定した発電をすることができる。   The wind is effectively used by the presence of the other wind receiving blade that receives the wind received by one wind receiving blade, and the first power gear 31a, the first opposing power gear 31b, the second power gear 31c, the second It is the same as that of the power generation device according to the first to fifth embodiments that the rotational torque of the opposing power gear 31d is increased. Therefore, even with the power generation apparatus according to the modification of the fifth embodiment, it is possible to effectively use the multipole generator with large internal resistance, and efficiently and stably generate power even in an environment where wind power is weak. Can.

（その他の実施の形態）
上記のように、本発明は第１〜第５の実施の形態によって記載したが、この開示の一部をなす論述及び図面は本発明を限定するものであると理解すべきではない。この開示から当業者には様々な代替実施の形態、実施例及び運用技術が明らかとなろう。例えば、発電装置の風受け羽根は、様々な形状の風受け羽根を用いることが可能である。図２７の斜視図に示すように、本発明の他の実施の形態に係る発電装置は、主回転軸３と、流体力（風力）により主回転軸３の周りを第１方向（図２７のＢ方向）に回転する第１の回転体２５ａと、第１の回転体２５ａが定義する第１の回転面と平行に対向する第２の回転面を有し、第２の回転面が第１方向と反対の第２方向（図２７のＡ方向）に、流体力（風力）により主回転軸３の周りを回転する第２の回転体２５ｂを備える。 (Other embodiments)
As described above, although the present invention has been described by the first to fifth embodiments, it should not be understood that the description and the drawings, which form a part of this disclosure, limit the present invention. Various alternative embodiments, examples and operation techniques will be apparent to those skilled in the art from this disclosure. For example, it is possible to use wind receiving blades of various shapes for the wind receiving blades of the power generation device. As shown in the perspective view of FIG. 27, the power generation apparatus according to another embodiment of the present invention has a main rotating shaft 3 and a fluid force (wind force) around the main rotating shaft 3 in a first direction (FIG. 27). B) has a first rotation body 25a rotating in the direction B), and a second rotation surface facing in parallel with a first rotation surface defined by the first rotation body 25a, the second rotation surface being a first rotation surface In a second direction (direction A in FIG. 27) opposite to the direction, a second rotating body 25b is provided which rotates around the main rotation axis 3 by fluid force (wind force).

他の実施の形態に係る発電装置は更に、第１の回転体２５ａ及び第２の回転体２５ｂの両者によって回転トルクが付与されて回転する第１の動力ギア３１ａと、第１の動力ギア３１ａの回転によって駆動される第１の発電機６２ａを備える。第１及び第２の回転面の定義は第１の実施の形態と同様である。   The power generation apparatus according to the other embodiment further includes a first power gear 31a that is rotated by applying a rotational torque by both the first rotating body 25a and the second rotating body 25b, and the first power gear 31a. And a first generator 62a driven by rotation of the The definitions of the first and second rotation surfaces are the same as in the first embodiment.

図２７の斜視図に示すように、主回転軸３は土台１に据え付けられ、重力方向に直立し、第２方向（図２７のＡ方向）に回転する。土台１の内部には、主回転軸３の回転エネルギーを取り出すための発電機が設置されていてもよい。   As shown in the perspective view of FIG. 27, the main rotary shaft 3 is mounted on the base 1, stands upright in the direction of gravity, and rotates in the second direction (direction A in FIG. 27). A generator for extracting rotational energy of the main rotation shaft 3 may be installed inside the base 1.

図２７に示すように、円筒面をなすベアリング５ａの外周面には、Ｔ字型に直交するように第１の支持棒９ａ及び第２の支持棒９ｂが固定されている。第１の支持棒９ａ及び第２の支持棒９ｂは互いに同一形状であり、長手方向は主回転軸３を挟んで互いに同一直線状に位置する。第１の支持棒９ａの外周側の端部に第１の風受け羽根１３ａが固定され、第２の支持棒９ｂの外周側の端部に第１の風受け羽根１３ａと同一形状の第２の風受け羽根１３ｂが、第１の風受け羽根１３ａとは風受け用の凹部を反対の向きになるように固定されている。第１の風受け羽根１３ａ及び第２の風受け羽根１３ｂの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第１の回転体２５ａは、風を受けると、ベアリング５ａごと第１方向（図２７のＢ方向）に回転する。   As shown in FIG. 27, a first support rod 9a and a second support rod 9b are fixed to the outer peripheral surface of the cylindrical bearing 5a so as to be orthogonal to the T-shape. The first support rods 9a and the second support rods 9b have the same shape, and the longitudinal directions are located on the same straight line with the main rotation shaft 3 interposed therebetween. The first wind receiving blade 13a is fixed to the outer circumferential end of the first support rod 9a, and the second wind receiving blade 13a has the same shape as the first wind receiving blade 13a at the outer circumferential end of the second support rod 9b. The wind receiving blade 13b is fixed so that the recess for receiving the wind is opposite to the first wind receiving blade 13a. The fixed locations of the first wind receiving blade 13 a and the second wind receiving blade 13 b are in a symmetrical positional relationship with respect to the main rotation axis 3. When the first rotating body 25a receives the wind, it rotates in the first direction (direction B in FIG. 27) together with the bearing 5a.

図２７に示すように、第２の回転体２５ｂにおいて、主回転軸３の長手方向にＴ字型に直交するように第３の支持棒９ｃ及び第４の支持棒９ｄが固定されている。第３の支持棒９ｃ及び第４の支持棒９ｄは互いに同一形状であり、長手方向は主回転軸３を挟んで互いに同一直線状に位置する第３の支持棒９ｃ及び第４の支持棒９ｄは第１の回転体２５ａの上方に位置する。第３の支持棒９ｃの外周側の端部に、第２の回転体２５ｂが第１の回転体２５ａと逆回転するような方向へ風受け用の凹部を向けて、第１の風受け羽根１３ａと同一形状の第３の風受け羽根１３ｃが固定されている。第４の支持棒９ｄの外周側の端部に、第３の風受け羽根１３ｃとは風受け用の凹部を反対の向きになるように、第１の風受け羽根１３ａと同一形状の第４の風受け羽根１３ｄが固定されている。第３の風受け羽根１３ｃ及び第４の風受け羽根１３ｄの固定箇所は、主回転軸３を挟んで対称の位置関係にある。第２の回転体２５ｂは、風を受けると第２方向（図２７のＡ方向）に回転する。   As shown in FIG. 27, in the second rotary body 25b, the third support rod 9c and the fourth support rod 9d are fixed so as to be orthogonal to the T-shape in the longitudinal direction of the main rotation shaft 3. The third support rod 9c and the fourth support rod 9d have the same shape, and the third support rod 9c and the fourth support rod 9d are arranged in the same straight line with the main rotary shaft 3 in the longitudinal direction. Is located above the first rotating body 25a. At the end on the outer peripheral side of the third support rod 9c, the concave for wind reception is directed in such a direction that the second rotary body 25b rotates in the reverse direction to the first rotary body 25a. A third wind receiving blade 13 c having the same shape as 13 a is fixed. A fourth support rod 9d has an end on the outer circumferential side, and a fourth same shape as the first wind receiving blade 13a so that the recess for wind receiving is opposite to the third wind receiving blade 13c. The wind receiving blade 13d is fixed. The fixing points of the third wind receiving blade 13 c and the fourth wind receiving blade 13 d are in a symmetrical positional relationship with the main rotation axis 3 interposed therebetween. The second rotating body 25b rotates in a second direction (direction A in FIG. 27) when wind is received.

第１の回転体２５ａの外周点は、図２７に示すように、第１の風受け羽根１３ａあるいは第２の風受け羽根１３ｂのいずれかの外周側の五角形型の側面のいずれかの頂点である。同様に、第２の回転体２５ｂの外周点は、第３の風受け羽根１３ｃあるいは第４の風受け羽根１３ｄのいずれかの外周側の五角形型の側面のいずれかの頂点となる。第１の回転体２５ａの外周点が描く外周円から定義される第１の回転面と、第２の回転体２５ｂの外周点が描く外周円から定義される第２の回転面とは、互いに平行に対向する関係である。   The outer peripheral point of the first rotating body 25a is, as shown in FIG. 27, an apex of one of the side faces of the pentagonal type on the outer peripheral side of either the first wind receiving blade 13a or the second wind receiving blade 13b. is there. Similarly, the outer peripheral point of the second rotating body 25b is an apex of one of the side faces of the pentagonal shape on the outer peripheral side of either the third wind receiving blade 13c or the fourth wind receiving blade 13d. The first rotation surface defined by the outer circumference circle drawn by the outer circumference point of the first rotation body 25a and the second rotation surface defined by the outer circumference circle drawn by the outer circumference point of the second rotation body 25b mutually It is a relation facing in parallel.

図２７に示すように、第１の動力ギア３１ａの歯及び第１の対向動力ギア３１ｂの歯は、第１の風受け羽根１３ａの上部及び第２の風受け羽根１３ｂの上部と、第３の風受け羽根１３ｃの下部及び第４の風受け羽根１３ｄの下部に設置されている。図２８及び図２９に示すように、第１の風受け羽根１３ａの上部には第１の風受け羽根１３ａと一体となった第１の突起７５ａ１及び７５ａ２が設けられている。第３の風受け羽根１３ｃの下部には第３の風受け羽根１３ｃと一体となった第２の突起７５ｂ１及び７５ｂ２が設けられている。図２９において、第１の動力ギア３１ａの歯は、第１の風受け羽根１３ａの上部の第１の突起７５ａ１及び７５ａ２、第３の風受け羽根１３ｃの下部の第２の突起７５ｂ１及び７５ｂ２とかみ合うように接触する。 As shown in FIG. 27, the teeth of the first power gear 31a and the teeth of the first opposing power gear 31b are the upper portion of the first wind receiving blade 13a and the upper portion of the second wind receiving blade 13b, and the third And the lower part of the fourth wind receiving blade 13 d. As shown in FIGS. 28 and 29, the upper portion of the first wind receiving blades 13a first projections 75a 1 and 75a 2 are provided integrated with the first wind receiving blades 13a. At the bottom of the third wind receiving blades 13c second projections 75b 1 and 75b 2 are provided integrated with the third wind receiving blades 13c. 29, the teeth of the first power gear 31a, the first wind receiving the first protrusion 75a 1 and 75a 2 of the upper wing 13a, a second protrusion 75b of the lower third of the wind receiving blades 13c 1 And 75b 2 to make contact.

図２９において、風を受けると、第１の風受け羽根１３ａは図２９に向かって左方向、第３の風受け羽根１３ｃは図２９に向かって右方向に動く。第１の風受け羽根１３ａ及び第３の風受け羽根１３ｃが動くに伴い、第１の動力ギア３１ａは第１の動力ギア回転軸６１ａを軸としてＡ方向に回転する。図２７の第１の対向動力ギア３１ｂも、第１の動力ギア３１ａと同様のしくみで回転する。第１の実施の形態に係る発電装置と同様、第１の動力ギア３１ａは、第１の回転体２５ａ及び第２の回転体２５ｂに接触し、両回転体から回転トルクを得ることになるので、１つの回転体しかない場合より、第１の動力ギア３１ａの回転力は大きくなる。第１の対向動力ギア３１ｂについても同様である。   In FIG. 29, when wind is received, the first wind receiving blade 13a moves to the left in FIG. 29 and the third wind receiving blade 13c moves to the right in FIG. As the first wind receiving blade 13a and the third wind receiving blade 13c move, the first power gear 31a rotates in the A direction about the first power gear rotation shaft 61a. The first opposing power gear 31b of FIG. 27 also rotates in the same manner as the first power gear 31a. As with the power generation apparatus according to the first embodiment, the first power gear 31a contacts the first rotating body 25a and the second rotating body 25b, and obtains rotational torque from both rotating bodies. The rotational force of the first power gear 31a is larger than when there is only one rotating body. The same applies to the first opposing power gear 31b.

一方の風受け羽根が受け流した風を受ける他方の風受け羽根の存在により、風が有効利用され、第１の動力ギア３１ａ及び第１の対向動力ギア３１ｂの回転トルクが大きくなることについても、第１の実施の形態に係る発電装置と同様である。   With regard to the fact that the wind is effectively used by the presence of the other wind receiving blade that receives the wind received by one of the wind receiving blades, and the rotational torque of the first power gear 31a and the first opposing power gear 31b is increased. It is the same as the power generation device according to the first embodiment.

他の実施の形態に係る発電装置の風受け羽根については、更に別の形状の風受け羽根を用いることが可能である。図３０はお椀型の風受け羽根の構造を示す。図３１はお椀型の変形タイプの風受け羽根の構造を示す。図３１の風受け羽根は、図３１（ｂ）及び図３１（ｄ）で示す尖端部に向かって、各辺が外側に湾曲した三角形を４つ張り合わせたような構造である。図３０及び図３１の風受け羽根はいずれも、風を受ける凹部と、上方又は下方に風を受け流す機能を有する凸部とを備える。   It is possible to use a wind receiving blade of another shape as the wind receiving blade of the power generation device according to the other embodiment. FIG. 30 shows the structure of a bowl-shaped wind receiving blade. FIG. 31 shows the structure of a bowl-shaped deformation type wind receiving blade. The wind receiving blade of FIG. 31 has a structure in which four triangles whose sides are curved outward are attached to each other toward the pointed end shown in FIGS. 31 (b) and 31 (d). Each of the wind receiving blades shown in FIGS. 30 and 31 includes a recess for receiving the wind and a protrusion having a function of letting the wind flow upward or downward.

風受け羽根の素材としては、合成樹脂（塩化ビニル、アクリル樹脂等）、合板、ＦＲＰ（繊維強化プラスチック）、金属、布等、様々な素材を使用することができる。比較的軽量であり、加工性に富み、風雨や紫外線による劣化等への耐久性等が求められる。特にＦＲＰは安価で軽量である上、強度や耐久性が高く、風受け羽根用素材として優れた素材である。流体力として水力などの水を用いる場合においても、水分や塩分などによる影響を考慮すると、羽根用素材には耐水性や耐腐食性に優れたＦＲＰなどを用いることが望ましい。また、水力発電や潮汐発電などでは、気体の数百倍の密度である液体の中で羽根を回転させる必要があることから、特に炭素繊維強化プラスチック（ＣＦＲＰ）などを用いて強度を高めることが好ましい。   As a material of the wind receiving blade, various materials such as synthetic resin (vinyl chloride, acrylic resin, etc.), plywood, FRP (fiber reinforced plastic), metal, cloth, etc. can be used. It is relatively lightweight, rich in processability, and required to be resistant to deterioration due to wind and rain and ultraviolet rays. In particular, FRP is inexpensive, lightweight, has high strength and durability, and is an excellent material as a material for wind vanes. Even when water such as hydraulic power is used as the fluid force, it is desirable to use FRP or the like excellent in water resistance and corrosion resistance as the material for the blade, in consideration of the influence of water and salt. In hydroelectric power generation, tidal power generation, etc., it is necessary to rotate the blades in a liquid having a density of several hundreds times that of gas, so carbon fiber reinforced plastic (CFRP) etc. may be used to increase strength. preferable.

なお、第１〜第５の実施の形態で説明したそれぞれの技術的思想を互いに組み合わせることも可能である。このように、本発明はここでは記載していない様々な実施の形態等を含むことは勿論である。したがって、本発明の技術的範囲は上記の説明から妥当と解釈しうる、特許請求の範囲に係る発明特定事項によってのみ定められるものである。   The technical ideas described in the first to fifth embodiments can be combined with each other. Thus, it is a matter of course that the present invention includes various embodiments and the like which are not described herein. Accordingly, the technical scope of the present invention is defined only by the invention-specifying matters according to the claims, which can be appropriately interpreted from the above description.

１…土台
３…主回転軸
５ａ、５ｂ…ベアリング
７ａ〜７ｄ…支柱
９ａ〜９ｈ…支持棒
１１ａ〜１１ｈ、 １３ａ〜１３ｄ…風受け羽根
２１ａ、２２ａ、２３ａ、２４ａ、２５ａ…第１の回転体
２１ｂ、２２ｂ、２３ｂ、２４ｂ、２５ｂ…第２の回転体
２１ｃ…第３の回転体
２１ｄ…第４の回転体
３１ａ…第１の動力ギア
３１ｂ…第１の対向動力ギア
３１ｃ…第２の動力ギア
３１ｄ…第２の対向動力ギア
３１ｅ…第３の動力ギア
３１ｆ…第３の対向動力ギア
４１ｉ、４２ｉ…歯先面
４３ｉａ、４３ｉｂ…歯面
４４ａ…（動力ギアの）上面
４４ｂ…（動力ギアの）下面
６１ａ…第１の動力ギア回転軸
６１ｂ…第１の対向動力ギア回転軸
６１ｃ…第２の動力ギア回転軸
６１ｄ…第２の対向動力ギア回転軸
６１ｅ…第３の動力ギア回転軸
６１ｆ…第３の対向動力ギア回転軸
６２ａ…第１の発電機
６２ｂ…第１の対向発電機
６２ｃ…第２の発電機
６２ｄ…第２の対向発電機
６２ｅ…第３の発電機
６２ｆ…第３の対向発電機
７１ａ１〜７１ａ９、７１ｂ１〜７１ｂ９ …… 駆動ギアの歯
７５ａ１、７５ａ２、７５ｂ１、７５ｂ２ …… （風受け羽根の）突起
８１ａ，８３ａ…第１の輪状フレーム
８１ｂ，８３ｂ…第２の輪状フレーム
８１ｃ…第３の輪状フレーム
８１ｄ…第４の輪状フレーム
８２ａ…第１の保持リング
８２ｂ…第２の保持リング
９１ａ、９１ｂ…溝 DESCRIPTION OF SYMBOLS 1 ... Base 3 ... Main rotating shaft 5a, 5b ... Bearing 7a-7d ... Support | pillar 9a-9h ... Support rod 11a-11h, 13a-13d ... Wind receiving blade 21a, 22a, 23a, 24a, 25a ... 1st rotary body 21b, 22b, 23b, 24b, 25b: second rotating body 21c: third rotating body 21d: fourth rotating body 31a: first power gear 31b: first opposing power gear 31c: second power gear 31d ... second opposing power gear 31e ... third power gear 31f ... third opposing power gear 41 i, 42 i ... tooth crest 43 ia, 43 ib ... tooth surfaces 44a ... (power gear) top 44b ... (the power gear) lower surface 61a ... first power gear rotary shaft 61b ... first opposing power gear rotary shaft 61c ... second power gear rotary shaft 61d ... second opposing power gear rotary shaft 61e ... third Power gear Rotary shaft 61f: third opposing power gear rotational shaft 62a: first generator 62b: first opposing generator 62c: second generator 62d: second opposing generator 62e: third generator 62f ... 3rd opposing generator 71a 1 to 71a 9 , 71b 1 to 71b 9 ...... Drive gear teeth 75a 1 , 75a 2 , 75b 1 , 75b 2 ...... Protrusions of wind receiving blades 81a, 83a ... 1st Second ring frame 81c third ring frame 81d fourth ring frame 82a first holding ring 82b second holding ring 91a, 91b groove

Claims (5)

主回転軸と、
流体力により前記主回転軸の周りを第１方向に回転する第１の回転体と、
前記第１の回転体が定義する第１の回転面と平行に対向する第２の回転面を有し、該第２の回転面が前記第１方向と反対の第２方向に、前記流体力により前記主回転軸の周りを回転する第２の回転体と、
前記第１の回転体及び第２の回転体の両者によって回転トルクが付与されて回転する第１の動力ギアと、
該第１の動力ギアの回転によって駆動される第１の発電機と、
を備えることを特徴とする発電装置。 With the main rotation axis,
A first rotating body that rotates in a first direction around the main rotation axis by a fluid force;
The fluid force has a second rotation surface facing in parallel with a first rotation surface defined by the first rotation body, the second rotation surface being in a second direction opposite to the first direction. A second rotating body that rotates around the main rotation axis by
A first power gear that is rotated by applying rotational torque by both the first and second rotating bodies;
A first generator driven by rotation of the first power gear;
A power generator comprising: 前記第１の回転体は、前記第１の回転面の一部を構成する第１の輪状フレームを前記第１の回転体の外周側に有し、
前記第２の回転体は、前記第２の回転面の一部を構成する第２の輪状フレームを前記第２の回転体の外周側に有することを特徴とする請求項１に記載の発電装置。 The first rotating body has a first ring-shaped frame forming a part of the first rotating surface on the outer peripheral side of the first rotating body,
2. The power generation device according to claim 1, wherein the second rotary body has a second ring-shaped frame forming a part of the second rotary surface on an outer peripheral side of the second rotary body. . 前記第１の回転体は、前記第１の輪状フレームの一方の面に放射状に歯を配列した第１の駆動ギアを更に有し、
前記第２の回転体は、前記第２の輪状フレームの前記第１の駆動ギアに平行に対向する面に、放射状に歯を配列した第２の駆動ギアを更に有し、
前記第１の動力ギアが、前記第１及び第２の駆動ギアの歯とかみ合って回転することを特徴とする請求項２に記載の発電装置。 The first rotating body further includes a first drive gear in which teeth are radially arranged on one surface of the first annular frame,
The second rotary body further includes a second drive gear in which teeth are radially arranged on a surface of the second annular frame facing in parallel to the first drive gear,
The power generation device according to claim 2, wherein the first power gear rotates in mesh with the teeth of the first and second drive gears. 前記第２の輪状フレームの前記第２の駆動ギアを有する面と反対側の面に放射状に歯を配列した第３の駆動ギアを、前記第２の輪状フレームが更に有することを特徴とする、請求項３に記載の発電装置。   The second annular frame further includes a third drive gear in which teeth are radially arranged on the side opposite to the side having the second drive gear of the second annular frame, The power generation device according to claim 3. 前記第２の輪状フレームと平行に対向する第３の輪状フレームを外周側に有し、前記第３の駆動ギアに平行に対向する前記第３の輪状フレームの面に放射状に歯を配列した第４の駆動ギアを有し、前記第３の輪状フレームが、前記流体力により前記主回転軸の周りを前記第１方向に回転する第３の回転体と、
前記外周側に配置され、前記第３及び第４の駆動ギアの歯とかみ合って回転する第２の動力ギアと、
該第２の動力ギアの回転によって駆動される第２の発電機と、
を更に備えることを特徴とする、請求項４に記載の発電装置。 A third annular frame facing in parallel to the second annular frame is provided on the outer peripheral side, and teeth are radially arranged on the surface of the third annular frame facing in parallel to the third drive gear A third rotating body having four driving gears, wherein the third ring-shaped frame is rotated in the first direction around the main rotation axis by the fluid force;
A second power gear disposed on the outer circumferential side and rotating in mesh with the teeth of the third and fourth drive gears;
A second generator driven by rotation of the second power gear;
The power generation apparatus according to claim 4, further comprising:
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