JP4751746B2 - Hydroelectric power generation apparatus and manufacturing method thereof - Google Patents

Hydroelectric power generation apparatus and manufacturing method thereof Download PDF

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JP4751746B2
JP4751746B2 JP2006085749A JP2006085749A JP4751746B2 JP 4751746 B2 JP4751746 B2 JP 4751746B2 JP 2006085749 A JP2006085749 A JP 2006085749A JP 2006085749 A JP2006085749 A JP 2006085749A JP 4751746 B2 JP4751746 B2 JP 4751746B2
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radial bearing
hole
shaft
cylindrical
cylindrical body
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JP2007262917A (en
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彰吾 田中
行宣 弓田
秀明 伊藤
伸一 吉川
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Nidec Sankyo Corp
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Nidec Sankyo Corp
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Priority to JP2006085749A priority Critical patent/JP4751746B2/en
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Priority to CN2011100372231A priority patent/CN102094745B/en
Priority to US11/728,759 priority patent/US7825531B2/en
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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
    • Y02P—CLIMATE CHANGE MITIGATION TECHNOLOGIES IN THE PRODUCTION OR PROCESSING OF GOODS
    • Y02P70/00—Climate change mitigation technologies in the production process for final industrial or consumer products
    • Y02P70/50—Manufacturing or production processes characterised by the final manufactured product

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  • Other Liquid Machine Or Engine Such As Wave Power Use (AREA)
  • Connection Of Motors, Electrical Generators, Mechanical Devices, And The Like (AREA)
  • Hydraulic Turbines (AREA)
  • Sliding-Contact Bearings (AREA)
  • Mounting Of Bearings Or Others (AREA)

Description

本発明は、水道水などを利用して発電を行う水力発電装置およびその製造方法に関するものである。   The present invention relates to a hydroelectric power generation apparatus that generates power using tap water or the like and a method for manufacturing the same.

蛇口の下方位置に手を差し出したとき、それをセンサが感知すると、蛇口から水を自動的に流すように構成した自動水栓装置が普及しつつある。また、近年、水道水の流路の途中位置に小型の水力発電装置を設けるとともに、この水力発電装置によって得た電力を蓄え、この電力を自動水栓装置のセンサ回路などに供給する装置も案出されている。   An automatic water faucet device configured to automatically flow water from a faucet when a sensor senses the hand when the hand is placed below the faucet is becoming widespread. In recent years, a small hydroelectric generator has been installed in the middle of the tap water flow path, and the electric power obtained by the hydroelectric generator has been stored and supplied to a sensor circuit of an automatic water faucet. Has been issued.

この種の水力発電装置は、流体入口から流体出口までの間に流路を構成するケースと、この流路の途中位置に配置された支軸と、この支軸に回転可能に支持された円筒状の発電用水車とを有しており、従来、発電用水車としては、外周面から羽根が張り出す円筒部に対して、支軸が貫通する軸穴をもつラジアル軸受が一体に樹脂成形されたものが用いられている（例えば、特許文献１参照）。
特開２００４−３４０１１１号公報 This type of hydroelectric generator includes a case that forms a flow path from a fluid inlet to a fluid outlet, a support shaft that is disposed in the middle of the flow path, and a cylinder that is rotatably supported by the support shaft. Conventionally, as a water turbine for power generation, a radial bearing having a shaft hole through which a support shaft passes is integrally molded with a cylindrical portion in which a blade projects from an outer peripheral surface. Is used (see, for example, Patent Document 1).
JP 2004-340111 A

しかしながら、発電用水車をラジアル軸受も含めて一体に樹脂成形すると、ヒケ等の影響により、軸穴の内径寸法に高い精度が得られず、発電用水車が回転したときに回転ノイズが発生するという問題点がある。また、外周面から羽根が張り出す円筒部の両端にラジアル軸受が各々、一体に樹脂成形されたものを採用しようとすると、ヒケ等の影響により、各ラジアル軸受の軸穴のサイズにばらつきが発生することがある。このような状態では、軸穴同士の同芯を出すことができないので、ラジアル軸受の軸穴と支軸との間に大きなクリアランスを設けることになるが、このような大きなクリアランスがあると、発電用水車が回転したときに回転ノイズが発生するという問題点がある。   However, if the water turbine for power generation is integrally resin-molded including radial bearings, high accuracy is not obtained in the inner diameter of the shaft hole due to the influence of sink marks and the like, and rotation noise is generated when the water turbine for power generation rotates. There is a problem. Also, if radial bearings are integrally molded on both ends of the cylindrical part where the blades protrude from the outer peripheral surface, the size of the shaft hole of each radial bearing will vary due to the influence of sink marks etc. There are things to do. In such a state, since the concentricity between the shaft holes cannot be obtained, a large clearance is provided between the shaft hole of the radial bearing and the support shaft. There is a problem that rotation noise occurs when the water turbine rotates.

以上の問題に鑑みて、本発明の課題は、発電用水車に設ける一対のラジアル軸受において軸穴同士の同芯を確実に出すことができる水力発電装置、およびその製造方法を提供することにある。   In view of the above problems, an object of the present invention is to provide a hydroelectric power generation device that can reliably bring out concentricity between shaft holes in a pair of radial bearings provided in a water turbine for power generation, and a method for manufacturing the same. .

上記課題を解決するために、本発明では、流体入口から流体出口に到る流路と、該流路の途中位置に配置された支軸と、該支軸に回転可能に支持された円筒状の発電用水車とを有する水力発電装置において、前記発電用水車は、外周面から羽根が張り出す樹脂成形品からなる円筒体と、該円筒体と別体に構成され、前記支軸が貫通する軸穴をもって前記円筒体の貫通穴の一方側端部に固定された円筒状の第１のラジアル軸受と、前記円筒体と別体に構成され、前記支軸が貫通する軸穴をもって前記貫通穴の他方側端部に固定された円筒状の第２のラジアル軸受とを備え、前記円筒体は、前記支軸の軸線方向において前記第１のラジアル軸受が位置する側に、前記軸線方向において前記第２のラジアル軸受が位置する側で筒状の永久磁石が外周に固着された上半部より大径かつ肉厚の下端部を備えており、当該下端部の外周に前記羽根が形成され、前記第１のラジアル軸受は、樹脂製ラジアル軸受であって、当該樹脂製ラジアル軸受では、前記軸穴を囲むように軸線方向に凹む周溝が形成され、前記軸穴と前記周溝との間には肉薄の円筒壁が構成されており、当該第１のラジアル軸受は、前記貫通穴内部のうち、前記下端部に対して半径方向内側に位置する部分に固定されていることを特徴とする。 In order to solve the above-mentioned problems, in the present invention, a flow path from a fluid inlet to a fluid outlet, a support shaft disposed at an intermediate position of the flow path, and a cylindrical shape rotatably supported by the support shaft In the hydraulic power generation apparatus having the power generation water turbine, the power generation water turbine is constituted by a cylindrical body made of a resin molded product in which blades protrude from an outer peripheral surface, and is separated from the cylindrical body, and the support shaft passes therethrough. A cylindrical first radial bearing fixed to one end portion of the through hole of the cylindrical body with an axial hole, and the cylindrical hole configured separately from the cylindrical body and having an axial hole through which the support shaft passes. Introduction of Bei and the other end which is fixed to a cylindrical second radial bearing, the cylindrical body, on the side where the in the axial direction of the support shaft first radial bearing is located in said axial direction On the side where the second radial bearing is located, a cylindrical permanent magnet A lower end portion having a diameter larger than that of the fixed upper half portion and having a thick wall; the blade is formed on an outer periphery of the lower end portion; and the first radial bearing is a resin radial bearing, and the resin In the manufactured radial bearing, a circumferential groove recessed in the axial direction is formed so as to surround the shaft hole, and a thin cylindrical wall is formed between the shaft hole and the circumferential groove, and the first radial bearing Is fixed to a portion located inside in the radial direction with respect to the lower end portion in the through hole .

本発明では、発電用水車を構成するにあたって、外周面から羽根が張り出す円筒体と、第１のラジアル軸受および第２のラジアル軸受とを別体で形成しているため、円筒体、第１のラジアル軸受および第２のラジアル軸受を樹脂成形品で構成した場合でもヒケ等が発生しにくい。従って、第１のラジアル軸受および第２のラジアル軸受のいずれにおいても、軸穴を高い寸法精度をもって樹脂成形することができる。また、円筒体に対して第１のラジアル軸受を固定した後、第１のラジアル軸受の軸穴を基準に第２のラジアル軸受の位置決めを行うことができるので、第１のラジアル軸受の軸穴と第２のラジアル軸受の軸穴とを同芯位置に配置することができる。それ故、発電用水車が回転した際の回転振動や回転ノイズの発生を確実に防止することができる。また、第１のラジアル軸受および第２のラジアル軸受については耐磨耗性材料で形成し、円筒体を安価な材料や軽量化に適した材料で形成することも可能であるため、ラジアル軸受を耐磨耗性材料で構成した場合でも製造コストを低く抑えることができる。また、第１のラジアル軸受は、軸穴を囲むように軸線方向に凹む周溝が形成された樹脂製ラジアル軸受であるため、第１のラジアル軸受を樹脂成形する際、樹脂製ラジアル軸受の内周面でのヒケを防止できる。それ故、樹脂製ラジアル軸受を製造した際、軸穴の径寸法により高い精度を得ることができる。また、樹脂製ラジアル軸受を円筒体の貫通穴に圧入した場合や溶着した場合でも、その変形が軸穴に影響を及ぼさないという利点がある。 In the present invention, since the cylindrical body in which the blades protrude from the outer peripheral surface and the first radial bearing and the second radial bearing are formed separately when the power generation water turbine is configured, the cylindrical body, the first Even when the radial bearing and the second radial bearing are made of a resin molded product, sink marks or the like are unlikely to occur. Therefore, in both the first radial bearing and the second radial bearing, the shaft hole can be resin-molded with high dimensional accuracy. In addition, since the second radial bearing can be positioned based on the shaft hole of the first radial bearing after the first radial bearing is fixed to the cylindrical body, the shaft hole of the first radial bearing And the shaft hole of the second radial bearing can be arranged at concentric positions. Therefore, it is possible to reliably prevent the occurrence of rotational vibration and rotational noise when the power generation water turbine rotates. Further, the first radial bearing and the second radial bearing can be formed of an abrasion-resistant material, and the cylindrical body can be formed of an inexpensive material or a material suitable for weight reduction. Even when it is made of an abrasion resistant material, the manufacturing cost can be kept low. Further, since the first radial bearing is a resin radial bearing in which a circumferential groove recessed in the axial direction is formed so as to surround the shaft hole, when the first radial bearing is molded with resin, Can prevent sink marks on the surface. Therefore, when a resin radial bearing is manufactured, high accuracy can be obtained by the diameter of the shaft hole. Further, even when a resin radial bearing is press-fitted into the through hole of the cylindrical body or welded, there is an advantage that the deformation does not affect the shaft hole.

本発明において、前記第２のラジアル軸受は、樹脂製ラジアル軸受であって、当該樹脂製ラジアル軸受では、前記軸穴を囲むように軸線方向に凹む周溝が形成され、前記軸穴と前記周溝との間には肉薄の円筒壁が構成されていることが好ましい。このように構成すると、第２のラジアル軸受を樹脂成形する際、樹脂製ラジアル軸受の内周面でのヒケを防止できる。それ故、樹脂製ラジアル軸受を製造した際、軸穴の径寸法により高い精度を得ることができる。また、樹脂製ラジアル軸受を円筒体の貫通穴に圧入した場合や溶着した場合でも、その変形が軸穴に影響を及ぼさないという利点がある。 In the present invention, the second radial bearing is a resin radial bearing, and in the resin radial bearing, a circumferential groove recessed in an axial direction is formed so as to surround the shaft hole, and the shaft hole and the circumferential A thin cylindrical wall is preferably formed between the grooves. If comprised in this way, when resin-molding a 2nd radial bearing , the sink on the internal peripheral surface of a resin-made radial bearing can be prevented. Therefore, when a resin radial bearing is manufactured, high accuracy can be obtained by the diameter of the shaft hole. Further, even when a resin radial bearing is press-fitted into the through hole of the cylindrical body or welded, there is an advantage that the deformation does not affect the shaft hole.

本発明において、前記第１のラジアル軸受を構成する前記樹脂製ラジアル軸受、および前記第２のラジアル軸受を構成する前記樹脂製ラジアル軸受のいずれにおいても、前記支軸との摺動部分の全体が前記円筒壁で構成されていることが好ましい。 In the present invention, in any of the resin radial bearing constituting the first radial bearing and the resin radial bearing constituting the second radial bearing, the entire sliding portion with the support shaft is It is preferable that the cylindrical wall is formed.

本発明において、前記貫通孔の他方側端部における内周面と前記第２のラジアル軸受の外周面とのクリアランスが、前記貫通孔の一方側端部における内周面と前記第１のラジアル軸受の外周面とのクリアランスより大きいことが好ましい。貫通孔の内周面と第１のラジアル軸受の外周面とのクリアランスが小さければ、第１のラジアル軸受については貫通穴に圧入でき、貫通孔の内周面と第２のラジアル軸受の外周面とのクリアランスが大きければ、第１のラジアル軸受の軸穴を基準に第２のラジアル軸受の位置決めを行う際、第２のラジアル軸受が貫通穴に当たって芯出しできないという事態を回避することができる。   In the present invention, the clearance between the inner peripheral surface at the other end portion of the through hole and the outer peripheral surface of the second radial bearing is such that the inner peripheral surface at the one end portion of the through hole and the first radial bearing. It is preferable that it is larger than the clearance with the outer peripheral surface. If the clearance between the inner peripheral surface of the through hole and the outer peripheral surface of the first radial bearing is small, the first radial bearing can be press-fitted into the through hole, and the inner peripheral surface of the through hole and the outer peripheral surface of the second radial bearing When the second radial bearing is positioned with reference to the shaft hole of the first radial bearing, it is possible to avoid a situation in which the second radial bearing hits the through hole and cannot be centered.

本発明に係る水力発電装置の製造方法において、前記第１のラジアル軸受および前記第２のラジアル軸受を前記円筒体に取り付けるにあたっては、前記円筒体の貫通穴の一方側端部に前記第１のラジアル軸受を固定する第１のラジアル軸受固定工程と、当該第１のラジアル軸受の軸穴を基準に前記第２のラジアル軸受を前記貫通穴の他方側端部で位置決めする芯出し工程と、前記第２のラジアル軸受を前記貫通穴の他方側端部に固定する第２のラジアル軸受固定工程とを行うことを特徴とする。 In the method for manufacturing a hydroelectric generator according to the present invention , when the first radial bearing and the second radial bearing are attached to the cylindrical body, the first radial bearing is attached to one end portion of the through hole of the cylindrical body. A first radial bearing fixing step of fixing the radial bearing; a centering step of positioning the second radial bearing at the other end of the through hole with reference to the shaft hole of the first radial bearing; And performing a second radial bearing fixing step of fixing the second radial bearing to the other end portion of the through hole.

本発明において、前記芯出し工程では、前記貫通穴の一方側端部に固定された前記第１のラジアル軸受の軸穴に位置決め軸を嵌めた後、当該位置決め軸を前記第２のラジアル軸受の軸穴に嵌めて当該第２のラジアル軸受を前記貫通穴の他方側端部で位置決めすることが好ましい。このように構成すれば、第１のラジアル軸受の軸穴を基準に第２のラジアル軸受の位置決めを容易にかつ、確実に行うことができる。   In the present invention, in the centering step, after the positioning shaft is fitted into the shaft hole of the first radial bearing fixed to one end of the through hole, the positioning shaft is attached to the second radial bearing. It is preferable that the second radial bearing is fitted to the shaft hole and positioned at the other end portion of the through hole. If comprised in this way, positioning of a 2nd radial bearing can be performed easily and reliably on the basis of the shaft hole of a 1st radial bearing.

本発明に係る水力発電装置では、発電用水車を構成するにあたって、外周面から羽根が張り出す円筒体と、第１のラジアル軸受および第２のラジアル軸受とを別体で形成しているため、円筒体、第１のラジアル軸受および第２のラジアル軸受を樹脂成形品で構成した場合でもヒケ等が発生しにくい。従って、第１のラジアル軸受および第２のラジアル軸受のいずれにおいても、軸穴を高い寸法精度をもって樹脂成形することができる。また、円筒体に対して第１のラジアル軸受を固定した後、第１のラジアル軸受の軸穴を基準に第２のラジアル軸受の位置決めを行うことができるので、第１のラジアル軸受の軸穴と第２のラジアル軸受の軸穴とを同芯位置に配置することができる。それ故、発電用水車が回転した際の回転振動や回転ノイズの発生を確実に防止することができる。また、第１のラジアル軸受および第２のラジアル軸受については耐磨耗性材料で形成し、円筒体を安価な材料で形成することも可能であるため、ラジアル軸受を耐磨耗性材料で構成した場合でも製造コストを低く抑えることができる。また、第１のラジアル軸受は、樹脂製ラジアル軸受であって、かかる樹脂製ラジアル軸受では、軸穴を囲むように軸線方向に凹む周溝が形成され、軸穴と前記周溝との間には肉薄の円筒壁が構成されている。このため、第１のラジアル軸受を樹脂成形する際、樹脂製ラジアル軸受の内周面でのヒケを防止できる。それ故、樹脂製ラジアル軸受を製造した際、軸穴の径寸法により高い精度を得ることができる。また、樹脂製ラジアル軸受を円筒体の貫通穴に圧入した場合や溶着した場合でも、その変形が軸穴に影響を及ぼさないという利点がある。 In the hydraulic power generation apparatus according to the present invention, when configuring the power generation water turbine, the cylindrical body from which the blades protrude from the outer peripheral surface, and the first radial bearing and the second radial bearing are formed separately. Even when the cylindrical body, the first radial bearing, and the second radial bearing are formed of a resin molded product, sink marks or the like are unlikely to occur. Therefore, in both the first radial bearing and the second radial bearing, the shaft hole can be resin-molded with high dimensional accuracy. In addition, since the second radial bearing can be positioned based on the shaft hole of the first radial bearing after the first radial bearing is fixed to the cylindrical body, the shaft hole of the first radial bearing And the shaft hole of the second radial bearing can be arranged at concentric positions. Therefore, it is possible to reliably prevent the occurrence of rotational vibration and rotational noise when the power generation water turbine rotates. In addition, the first radial bearing and the second radial bearing can be made of an abrasion resistant material, and the cylindrical body can be made of an inexpensive material, so the radial bearing is made of an abrasion resistant material. Even in this case, the manufacturing cost can be kept low. Further, the first radial bearing is a resin radial bearing, and in the resin radial bearing, a circumferential groove that is recessed in an axial direction is formed so as to surround the shaft hole, and between the shaft hole and the circumferential groove. Has a thin cylindrical wall. For this reason, when resin-molding a 1st radial bearing, the sink on the internal peripheral surface of a resin-made radial bearing can be prevented. Therefore, when a resin radial bearing is manufactured, high accuracy can be obtained by the diameter of the shaft hole. Further, even when a resin radial bearing is press-fitted into the through hole of the cylindrical body or welded, there is an advantage that the deformation does not affect the shaft hole.

以下に、図面を参照して、本発明を適用した水力発電装置およびその製造方法を説明する。   Below, with reference to drawings, the hydroelectric generator to which this invention is applied, and its manufacturing method are demonstrated.

（全体構成）
図１（ａ）、（ｂ）は、本発明を適用した水力発電装置の平面図、およびＡ−Ａ′断面図である。なお、Ａ−Ａ′線は、射出口の形成位置を通らないが、図１（ｂ）の左部分には、射出口についても図示してある。 (overall structure)
1A and 1B are a plan view and a cross-sectional view taken along line AA ′ of a hydroelectric power generation apparatus to which the present invention is applied. The AA ′ line does not pass through the injection port formation position, but the injection port is also shown in the left part of FIG.

図１（ａ）、（ｂ）に示す水力発電装置１は、水道水の流路の途中位置になどに配置される小型の水力発電装置であり、この水力発電装置１によって得た電力を蓄え、この電力を自動水栓装置のセンサ回路などに供給する用途などに用いられる。本形態の水力発電装置１は、後述する流路を構成する樹脂製の本体ケース２１、この本体ケース２１の上面を覆うカバー２３、このカバー２３を覆うステンレス製のカップ状の仕切り板２５と、この仕切り板２５のフランジ部との間にステータ部６を挟む環状ケース２７と、環状ケース２７の上方に被さる樹脂製の上ケース２９とを有しており、上ケース２９および仕切り板２５はネジにより本体ケース２１に固定されている。また、本体ケース２１の底面にはＥＰＤＭ製のシール２８１が重ねられ、仕切り板２５と本体ケース２１との間には、ゴム製のＯリング２８２が配置されている。   A hydroelectric generator 1 shown in FIGS. 1 (a) and 1 (b) is a small hydroelectric generator arranged at a midway position in the flow path of tap water, and stores electric power obtained by the hydroelectric generator 1. It is used for the purpose of supplying this power to a sensor circuit of an automatic faucet device. The hydroelectric generator 1 of the present embodiment includes a resin-made main body case 21 constituting a flow path to be described later, a cover 23 that covers the upper surface of the main body case 21, a stainless cup-shaped partition plate 25 that covers the cover 23, An annular case 27 sandwiching the stator portion 6 between the flange portion of the partition plate 25 and a resin upper case 29 covering the annular case 27 are provided. The upper case 29 and the partition plate 25 are screwed. Is fixed to the main body case 21. An EPDM seal 281 is stacked on the bottom surface of the main body case 21, and a rubber O-ring 282 is disposed between the partition plate 25 and the main body case 21.

本体ケース２１には、相対向する側面で開口する流体入口３１および流体出口３２を備えており、流体入口３１から流体出口３２に向かう流路（矢印Ｌで示す）の途中位置には、本体ケース２１とカバー２３とにより、後述する注水部が構成され、本体ケース２１と仕切り板２５との間に水車室３５が構成されている。水車室３５では、下端部および上端部が各々、本体ケース２１および仕切り板２５の軸固定穴に圧入固定された支軸４が直立しており、支軸４には、円筒状の発電用水車５が回転可能に支持されている。支軸４には、樹脂製のスリーブ４５が嵌められており、発電用水車５は、支軸４のうち、スリーブ４５から露出している上半部で支持されている。なお、発電用水車５は、支軸４に装着されたワッシャなどにより上下方向への変位が防止されている。   The main body case 21 is provided with a fluid inlet 31 and a fluid outlet 32 that open on opposite side surfaces, and the main body case is located in the middle of a flow path (indicated by an arrow L) from the fluid inlet 31 to the fluid outlet 32. 21 and the cover 23 form a water injection section described later, and a water turbine chamber 35 is formed between the main body case 21 and the partition plate 25. In the water turbine chamber 35, the lower end and the upper end are respectively upright with the support shaft 4 press-fitted and fixed in the shaft fixing holes of the main body case 21 and the partition plate 25, and the support shaft 4 has a cylindrical power generation water turbine. 5 is rotatably supported. A resin sleeve 45 is fitted to the support shaft 4, and the power generation water turbine 5 is supported by the upper half of the support shaft 4 exposed from the sleeve 45. The power generation water turbine 5 is prevented from being displaced in the vertical direction by a washer or the like attached to the support shaft 4.

発電用水車５において仕切り板２５の円筒部２５１内に位置する上半部には、外周面に円筒状の永久磁石５５が固着されている。また、仕切り板２５の円筒部２５１の周りには環状のステータ組６１、６２が配置されており、永久磁石５５およびステータ部６によって発電部が構成されている。   A cylindrical permanent magnet 55 is fixed to the outer peripheral surface of the upper half portion of the power generation water turbine 5 located in the cylindrical portion 251 of the partition plate 25. In addition, annular stator sets 61 and 62 are disposed around the cylindrical portion 251 of the partition plate 25, and a power generation unit is configured by the permanent magnet 55 and the stator unit 6.

（発電部の構成）
ステータ部６は、軸線方向に重ねて配置された２つの相のステータ組６１、６２で構成されている。２つのステータ組６１、６２のいずれにおいても、外ステータコア、コイルボビンに巻回されたコイル、および内ステータコアが重ねられた構造を有しており、コイルボビンの内周に沿って、外ステータコアの極歯と内ステータコアの極歯が交互に並んでいる。また、コイルの巻き始め部分および巻き終わり部分は、端子台６６の端子６７およびワイヤー６８を介してコネクタ６９に接続されている。なお、上ケース２９には、端子台６６を覆うフード部２９１が形成されており、ステータ部６に水が浸入するのを防止する構造になっている。 (Configuration of power generation unit)
The stator portion 6 is composed of two-phase stator sets 61 and 62 that are arranged so as to overlap in the axial direction. Each of the two stator sets 61 and 62 has a structure in which an outer stator core, a coil wound around a coil bobbin, and an inner stator core are stacked, and pole teeth of the outer stator core are arranged along the inner circumference of the coil bobbin. And the pole teeth of the inner stator core are arranged alternately. Further, the winding start portion and winding end portion of the coil are connected to the connector 69 via the terminal 67 and the wire 68 of the terminal block 66. The upper case 29 is formed with a hood portion 291 that covers the terminal block 66, and has a structure that prevents water from entering the stator portion 6.

（注水部およびバイパス流路の構成）
本形態の水力発電装置１において、本体ケース２１では、流体入口３１に対向するように隔壁２１９が起立しており、その上方には、水車室３５の周りに環状流路３３が形成されている。ここで、環状流路３３は、底面、内周面、外周面、および上面が各々、本体ケース２１の環状の仕切り壁２１１、本体ケース２１の環状の内側垂直壁２１２、本体ケース２１の環状の外側垂直壁２１３、およびカバー２３により規定されている。 (Configuration of water injection section and bypass flow path)
In the hydroelectric generator 1 of this embodiment, in the main body case 21, a partition wall 219 is erected so as to face the fluid inlet 31, and an annular flow path 33 is formed around the water turbine chamber 35 above the partition wall 219. . Here, the annular flow path 33 has a bottom surface, an inner circumferential surface, an outer circumferential surface, and an upper surface, respectively, an annular partition wall 211 of the main body case 21, an annular inner vertical wall 212 of the main body case 21, and an annular shape of the main body case 21. It is defined by the outer vertical wall 213 and the cover 23.

ここで、内側垂直壁２１２には、周方向の複数箇所、例えば、４箇所に切り欠きが形成されており、本体ケース２１の上面にカバー２３を被せると、４つの切り欠きによって、環状流路３３から発電用水車５の羽根５７に向けて水を高速噴射する４つの射出口３４が構成される。   Here, the inner vertical wall 212 has notches formed at a plurality of circumferential positions, for example, four places. When the cover 23 is placed on the upper surface of the main body case 21, the four notches form an annular flow path. Four injection ports 34 for injecting water at high speed from 33 toward the blades 57 of the power generation water turbine 5 are configured.

なお、隔壁２１９には、流体入口３１から流入した水を環状流路３３を通らずに流体出口３２に向かわせるバイパス用の開口３８が形成されており、この開口３８は、隔壁２１９の裏面側に配置されたスライダ９０により塞がれている。隔壁２１９には流体入口３１に向けて延びた円筒部２１７を有する一方、スライダ９０は、隔壁２１９の裏面に樹脂製シール９６を介して当接する板状の弁部９０１と、弁部９０１から円筒部２１７内に延びた軸部９０２と、軸部９０２の先端部にプッシュナット９１により固定されたワッシャ９２とを備えており、円筒部２１７の端部とワッシャ９２との間にはコイルバネ９５が配置されている。従って、流体入口３１から流入した水の圧力が低い場合には、スライダ９０は、コルイバネ９５に付勢されて弁部９０１が隔壁２１９に当接しているので、バイパス用の開口３８は閉鎖されている。但し、流体入口３１から流入した水の圧力が高く、ワッシャ９２がコイルバネ９５の付勢力よりも大きな水圧を受けると、スライダ９０は、弁部９０１が隔壁２１９から離間する方向に変位し、バイパス用の開口３８は開放される。それ故、流体入口３１から流入した水の圧力が低い場合には、流入した水の全てが環状流路３３に導かれる一方、流体入口３１から流入した水の圧力が高い場合には、流入した水の一部が環状流路３３に導かれずにバイパス用の開口３８を通ってそのまま流体出口３２に向かうことになる。従って、流入する水の圧力が過剰に高くなった場合でも、環状流路３３を介して水車室３５に導入される水量を規制することができるので、回転ノイズなどの発生を防止することができる。   The partition wall 219 is provided with a bypass opening 38 that allows water flowing from the fluid inlet 31 to be directed to the fluid outlet 32 without passing through the annular flow path 33, and this opening 38 is formed on the back surface side of the partition wall 219. It is blocked by a slider 90 arranged at the position. The partition wall 219 has a cylindrical portion 217 extending toward the fluid inlet 31, while the slider 90 has a plate-like valve portion 901 that abuts the back surface of the partition wall 219 via a resin seal 96, and the valve portion 901 has a cylindrical shape. A shaft portion 902 extending into the portion 217, and a washer 92 fixed to the tip of the shaft portion 902 by a push nut 91. A coil spring 95 is interposed between the end portion of the cylindrical portion 217 and the washer 92. Has been placed. Therefore, when the pressure of the water flowing in from the fluid inlet 31 is low, the slider 90 is urged by the coil spring 95 and the valve portion 901 is in contact with the partition wall 219, so that the bypass opening 38 is closed. Yes. However, when the pressure of the water flowing in from the fluid inlet 31 is high and the washer 92 receives a water pressure larger than the urging force of the coil spring 95, the slider 90 is displaced in the direction in which the valve portion 901 is separated from the partition wall 219, thereby bypassing. The opening 38 is opened. Therefore, when the pressure of water flowing in from the fluid inlet 31 is low, all of the water flowing in is guided to the annular flow path 33, whereas when the pressure of water flowing in from the fluid inlet 31 is high, it flows in A part of the water is not guided to the annular flow path 33, but goes directly to the fluid outlet 32 through the bypass opening 38. Therefore, even when the pressure of the inflowing water becomes excessively high, the amount of water introduced into the water turbine chamber 35 via the annular flow path 33 can be regulated, so that generation of rotational noise and the like can be prevented. .

（発電用水車５の構成）
図２（ａ）、（ｂ）、（ｃ）は、図１に示す水力発電装置に用いた発電用水車を第１のラジアル軸受側からみたときの斜視図、この発電用水車を第２のラジアル軸受側からみたときの平面図、およびＢ−Ｂ′断面図である。 (Configuration of water turbine 5 for power generation)
2 (a), 2 (b), and 2 (c) are perspective views of the power generation turbine used in the hydroelectric generator shown in FIG. 1 as viewed from the first radial bearing side. It is the top view when seen from the radial bearing side, and BB 'sectional drawing.

図２（ａ）、（ｂ）、（ｃ）に示すように、本形態の水力発電装置１において、発電用水車５は、外周面から複数枚の羽根５７が等角度間隔で張り出す円筒体５０と、この円筒体５０の貫通穴５０１の一方側端部（本体ケース２１が位置する下方側）に位置する円筒状の第１のラジアル軸受５１と、貫通穴５０１の他方側端部（仕切り板２５の円筒部２５１が位置する上方側）に位置する円筒状の第２のラジアル軸受５２とを備えており、第１のラジアル軸受５１の軸穴５１０、および第２のラジアル軸受５２の軸穴５２０に対して、図１（ｂ）に示す支軸４が嵌ることにより、発電用水車５は支軸４の周りで回転可能に支持されている。円筒体５０は、羽根５７が形成された下端部は大径である一方、上半部は小径であり、この小径部分に円筒状の永久磁石５５が固定されている。   As shown in FIGS. 2 (a), (b), and (c), in the hydroelectric generator 1 of this embodiment, the power generation water turbine 5 is a cylindrical body in which a plurality of blades 57 project from the outer peripheral surface at equal angular intervals. 50, a cylindrical first radial bearing 51 located at one end of the through hole 501 of the cylindrical body 50 (a lower side where the main body case 21 is located), and the other end of the through hole 501 (partition And a cylindrical second radial bearing 52 positioned on the upper side where the cylindrical portion 251 of the plate 25 is located, and the shaft hole 510 of the first radial bearing 51 and the shaft of the second radial bearing 52. The power generation water turbine 5 is rotatably supported around the support shaft 4 by fitting the support shaft 4 shown in FIG. The cylindrical body 50 has a large diameter at the lower end where the blades 57 are formed, and a small diameter at the upper half, and a cylindrical permanent magnet 55 is fixed to the small diameter portion.

本形態において、発電用水車５では、複数枚の羽根５７が各々、軸線方向で上側羽根部５７１と下側羽根部５７２とに２分割されており、下側羽根部５７２の外周端は、円筒体５０の軸線方向と平行な円筒板部５８により連結されている。   In this embodiment, in the power generation turbine 5, the plurality of blades 57 are each divided into two in the axial direction into an upper blade portion 571 and a lower blade portion 572, and the outer peripheral end of the lower blade portion 572 is cylindrical. They are connected by a cylindrical plate portion 58 parallel to the axial direction of the body 50.

このように構成した発電用水車５に対しては、図２（ｂ）、（ｃ）に示すように、４つの射出口３４が発電用水車５の周りに等角度間隔に形成されており、図２（ｃ）に矢印Ｌ１、Ｌ２で示すように、４つの射出口３４は各々、上側羽根部５７１と円筒板部５８とに跨って水を射出するように構成されている。すなわち、射出口３４から射出された水の一部は、矢印Ｌ１で示すように、上側羽根部５７１に直接、ぶつかる一方、射出口３４から射出された水の残りは、円筒板部５８の外周面にぶつかるようになっている。   As shown in FIGS. 2B and 2C, for the power generation water turbine 5 configured as described above, four injection ports 34 are formed around the power generation water wheel 5 at equal angular intervals. As shown by arrows L 1 and L 2 in FIG. 2C, each of the four injection ports 34 is configured to inject water across the upper blade portion 571 and the cylindrical plate portion 58. That is, a part of the water ejected from the ejection port 34 directly collides with the upper blade portion 571 as indicated by an arrow L1, while the remaining water ejected from the ejection port 34 is the outer periphery of the cylindrical plate portion 58. It hits the surface.

また、本形態において、注水部に形成した射出口３４の数と羽根５７の枚数とは、素の関係にあり、一方が他方の整数倍となる条件を避けてある。例えば、本形態では、射出口３４は４つであるのに対して、羽根５７の枚数は７枚である。   Further, in this embodiment, the number of injection ports 34 formed in the water injection section and the number of blades 57 are in a prime relationship, and the condition that one is an integral multiple of the other is avoided. For example, in this embodiment, the number of the ejection ports 34 is four, while the number of the blades 57 is seven.

本形態において、第１のラジアル軸受５１および第２のラジアル軸受５２はいずれも、円筒体５０とは別体の樹脂成形品であり、第１のラジアル軸受５１は、貫通穴５０１の一方側端部に圧入後、円筒体５０に溶着されて貫通穴５０１内に固定されている。従って、貫通穴５０１の一方側端部における内周面と第１のラジアル軸受５１の外周面とのクリアランスは、例えば、０〜０．０３ｍｍと小さい。これに対して、第２のラジアル軸受５２は、後述するように、第１のラジアル軸受５１の軸穴５１０を基準にラジアル方向で位置決めされた状態で貫通穴５０１内に挿入され、円筒体５０に溶着されている。このため、第２のラジアル軸受５２を第１のラジアル軸受５１の軸穴５１０を基準にラジアル方向で位置決めする際、貫通穴５０１内でラジアル方向で位置調整が可能なように、貫通穴５０１の他方側端部における内周面と第２のラジアル軸受５２の外周面とのクリアランスは、例えば、０．０４〜０．０７ｍｍと大きく設定されている。   In this embodiment, both the first radial bearing 51 and the second radial bearing 52 are resin molded products that are separate from the cylindrical body 50, and the first radial bearing 51 is at one end of the through hole 501. After being press-fitted into the part, it is welded to the cylindrical body 50 and fixed in the through hole 501. Therefore, the clearance between the inner peripheral surface at one end of the through hole 501 and the outer peripheral surface of the first radial bearing 51 is as small as 0 to 0.03 mm, for example. On the other hand, the second radial bearing 52 is inserted into the through hole 501 in a state of being positioned in the radial direction with reference to the shaft hole 510 of the first radial bearing 51, as will be described later. It is welded to. For this reason, when the second radial bearing 52 is positioned in the radial direction with respect to the shaft hole 510 of the first radial bearing 51, the position of the through hole 501 is adjusted so that the position in the through hole 501 can be adjusted in the radial direction. The clearance between the inner peripheral surface at the other end and the outer peripheral surface of the second radial bearing 52 is set large, for example, 0.04 to 0.07 mm.

（水力発電装置１１の製造方法）
以下、図１、図２および図３を参照して、本形態の水力発電装置１の製造方法のうち、発電用水車５の組み立て方法を説明しながら、発電用水車５の構成を詳述する。 (Manufacturing method of the hydroelectric generator 11)
Hereinafter, with reference to FIGS. 1, 2, and 3, the configuration of the power generation water turbine 5 will be described in detail while explaining the method of assembling the power generation water turbine 5 in the method of manufacturing the hydroelectric power generator 1 of the present embodiment. .

図３（ａ）〜（ｄ）は、図２に示す発電用水車の組み立て方法を示す工程断面図である。まず、図３（ａ）に示すように、円筒体５０では、下端面に４枚の板状の溶着用突起５０６が形成されており、これらの溶着用突起５０６は、貫通穴５０１の内周縁に沿って等角度間隔に形成されている。これに対して、第１のラジアル軸受５１は、下端寄りの位置で拡径する円盤状のフランジ部５１４が形成されており、このフランジ部５１４の付け根部分には、円筒体の溶着用突起５０６が嵌る４つの穴５１５が形成されている。また、第１のラジアル軸受５１の下端面では、穴５１５が形成されている位置より内周側で軸穴５１０を囲むように軸線方向に凹む周溝５１８が開口しており、軸穴５１０と周溝５１８との間には肉薄の円筒壁５１９が形成されている。ここで、軸穴５１０は、軸線方向で内径が切り換わっており、内径が小さい部分が支軸４との摺動部分５１１であるため、周溝５１８は、摺動部分５１１の全体を肉薄の円筒壁５１９で構成する深さに形成されている。   3A to 3D are process cross-sectional views illustrating a method for assembling the power generation turbine shown in FIG. First, as shown in FIG. 3A, in the cylindrical body 50, four plate-like welding projections 506 are formed on the lower end surface, and these welding projections 506 are the inner periphery of the through hole 501. Are formed at equiangular intervals. On the other hand, the first radial bearing 51 is formed with a disk-like flange portion 514 whose diameter is enlarged near the lower end. A cylindrical welding protrusion 506 is formed at the base portion of the flange portion 514. Four holes 515 into which are fitted are formed. Further, on the lower end surface of the first radial bearing 51, a circumferential groove 518 that is recessed in the axial direction is opened so as to surround the shaft hole 510 on the inner peripheral side from the position where the hole 515 is formed. A thin cylindrical wall 519 is formed between the circumferential groove 518. Here, since the inner diameter of the shaft hole 510 is switched in the axial direction, and the portion with the smaller inner diameter is the sliding portion 511 with the support shaft 4, the circumferential groove 518 has a thin entire sliding portion 511. A depth formed by the cylindrical wall 519 is formed.

また、円筒体５０では、上端面に３枚の板状の溶着用突起５０７が形成されており、これらの溶着用突起５０７は、貫通穴５０１の内周縁に沿って等角度間隔に形成されている。これに対して、第２のラジアル軸受５２は、上端寄りの位置で拡径する円盤状のフランジ部５２４が形成されており、このフランジ部５２４の付け根部分には、円筒体の溶着用突起５０７が嵌る３つの穴５２５が形成されている。また、第２のラジアル軸受５２の上端面には、穴５２５が形成されている位置より内周側で軸穴５２０を囲むように軸線方向に凹む周溝５２８が開口しており、軸穴５２０と周溝５２８との間には肉薄の円筒壁５２９が形成されている。ここで、軸穴５２０は、軸線方向で内径が切り換わっており、内径が小さい部分が支軸４との摺動部分５２１であるため、周溝５２８は、摺動部分５２１の全体を肉薄の円筒壁５２９で構成する深さに形成されている。   Further, in the cylindrical body 50, three plate-like welding protrusions 507 are formed on the upper end surface, and these welding protrusions 507 are formed at equal angular intervals along the inner peripheral edge of the through hole 501. Yes. On the other hand, the second radial bearing 52 is formed with a disk-like flange portion 524 whose diameter is increased near the upper end, and a cylindrical welding protrusion 507 is formed at the base portion of the flange portion 524. Three holes 525 are formed in which to fit. Further, a circumferential groove 528 that is recessed in the axial direction is opened on the upper end surface of the second radial bearing 52 so as to surround the shaft hole 520 on the inner peripheral side from the position where the hole 525 is formed. A thin cylindrical wall 529 is formed between the peripheral groove 528 and the circumferential groove 528. Here, since the inner diameter of the shaft hole 520 is switched in the axial direction, and the portion with the smaller inner diameter is the sliding portion 521 with the support shaft 4, the circumferential groove 528 has a thin entire sliding portion 521. A depth formed by the cylindrical wall 529 is formed.

このように構成した円筒体５０、第１のラジアル軸受５１、および第２のラジアル軸受５２を用いて発電用水車５を組み立てるにあたっては、まず、図３（ｂ）に示す第１のラジアル軸受固定工程において、円筒体５０の下端面に形成した溶着用突起５０６が第１のラジアル軸受５１の穴５１５に嵌るように、第１のラジアル軸受５１を貫通穴５０１の一方側端部に圧入した後、穴５１５から突き出た溶着用突起５０６の先端部を加熱溶融し、第１のラジアル軸受５１を貫通穴５０１の一方側端部に溶着により固定する。   In assembling the power generation turbine 5 using the cylindrical body 50, the first radial bearing 51, and the second radial bearing 52 configured as described above, first, the first radial bearing fixing shown in FIG. In the process, after the first radial bearing 51 is press-fitted into one end of the through hole 501 so that the welding protrusion 506 formed on the lower end surface of the cylindrical body 50 fits into the hole 515 of the first radial bearing 51. The tip end portion of the welding projection 506 protruding from the hole 515 is heated and melted, and the first radial bearing 51 is fixed to one end portion of the through hole 501 by welding.

次に、芯出し工程では、図３（ｃ）に示すように、貫通穴５０１の一方側端部に固定された第１のラジアル軸受５１の軸穴５１０に位置決め軸９を嵌めた後、位置決め軸９を第２のラジアル軸受５２の軸穴５２０に嵌めて、図３（ｄ）に示すように、第２のラジアル軸受５２を貫通穴５０１の他方側端部に挿入する。その際、円筒体５０の上端面に形成した溶着用突起５０７を第２のラジアル軸受５２のフランジ部５２４に形成した穴５２５に嵌める。ここで、貫通穴５０１の内周面と第２のラジアル軸受５２の外周面とのクリアランスは、例えば、０．０４〜０．０７ｍｍと大きく設定されているため、第２のラジアル軸受５２を第１のラジアル軸受５１の軸穴５１０を基準にラジアル方向で位置決めする際、貫通穴５０１内でラジアル方向で第２のラジアル軸受５２の位置調整が可能である。なお、穴５２５と溶着用突起５０７との間にも十分なクリアランスが設定されている。   Next, in the centering step, as shown in FIG. 3C, the positioning shaft 9 is fitted into the shaft hole 510 of the first radial bearing 51 fixed to one end of the through hole 501, and then the positioning is performed. The shaft 9 is fitted into the shaft hole 520 of the second radial bearing 52, and the second radial bearing 52 is inserted into the other end of the through hole 501 as shown in FIG. At that time, the welding protrusion 507 formed on the upper end surface of the cylindrical body 50 is fitted into the hole 525 formed in the flange portion 524 of the second radial bearing 52. Here, since the clearance between the inner peripheral surface of the through hole 501 and the outer peripheral surface of the second radial bearing 52 is set to be as large as, for example, 0.04 to 0.07 mm, the second radial bearing 52 can be When positioning in the radial direction with respect to the shaft hole 510 of the first radial bearing 51, the position of the second radial bearing 52 can be adjusted in the radial direction in the through hole 501. A sufficient clearance is also set between the hole 525 and the welding projection 507.

次に、第２のラジアル軸受固定工程において、穴５２５から突き出た溶着用突起５０７の先端部を加熱溶融し、第２のラジアル軸受５２を貫通穴５０１の他方側端部に溶着により固定する。このように固定した第２のラジアル軸受５２は、永久磁石５５が円筒体５０から脱落することを防止する機能も担うことになる。   Next, in the second radial bearing fixing step, the tip end portion of the welding projection 507 protruding from the hole 525 is heated and melted, and the second radial bearing 52 is fixed to the other end portion of the through hole 501 by welding. The second radial bearing 52 fixed in this way also has a function of preventing the permanent magnet 55 from falling off the cylindrical body 50.

しかる後には、位置決め軸９を抜く。このように構成した発電用水車５については、水力発電装置１を組み立てる際、第１のラジアル軸受５１の軸穴５１０、および第２のラジアル軸受５２の軸穴５２０に支軸４が嵌った状態で水車室３５に配置される。   After that, the positioning shaft 9 is pulled out. Regarding the power generation turbine 5 configured in this way, when the hydroelectric generator 1 is assembled, the support shaft 4 is fitted in the shaft hole 510 of the first radial bearing 51 and the shaft hole 520 of the second radial bearing 52. Is disposed in the watermill 35.

（動作）
このように構成した水力発電装置１において、流体入口３１から流れ込んだ水は、隔壁にぶつかって上方の環状流路３３に流れ込んだ後、４つの射出口３４から発電用水車５の羽根５７に向けて射出される。その結果、発電用水車５が回転し、それに伴い、永久磁石５５も回転することにより、ステータ部６のコイルに誘起電圧が発生する。発電用水車５を回し終えた水は、下方に落下し、そこから流体出口３２を経て排出される。また、ステータ部６で発生した誘起電圧は、コネクタ６９を介して外部の回路に導かれ、この回路で直流に変換された後、整流され電池に充電される。 (Operation)
In the hydroelectric generator 1 configured as described above, the water flowing in from the fluid inlet 31 collides with the partition wall and flows into the upper annular flow path 33, and then from the four outlets 34 toward the blades 57 of the power generation turbine 5. And injected. As a result, the power generation water turbine 5 rotates, and accordingly, the permanent magnet 55 also rotates, so that an induced voltage is generated in the coil of the stator portion 6. The water that has finished turning the power generation water turbine 5 falls downward and is discharged therefrom through the fluid outlet 32. The induced voltage generated in the stator unit 6 is guided to an external circuit via the connector 69, converted into direct current by this circuit, and then rectified and charged to the battery.

（本形態の主な効果）
以上説明したように、本形態の水力発電装置１では、発電用水車５を構成するにあたって、外周面から羽根５７が張り出す円筒体５０と、第１のラジアル軸受５１および第２のラジアル軸受５２とを別体で形成しているため、円筒体５０、第１のラジアル軸受５１および第２のラジアル軸受５２を樹脂成形品で構成した場合でも、ヒケ等が発生しにくい。それ故、双方の軸穴５１０、５２０が高い寸法精度をもって同一サイズとなるように、第１のラジアル軸受５１および第２のラジアル軸受５２を樹脂成形により製造できる。また、円筒体５０に対して第１のラジアル軸受５１を固定した後、第１のラジアル軸受５１の軸穴５１０を基準に第２のラジアル軸受５２の位置決めを行うので、第１のラジアル軸受５１と第２のラジアル軸受５２とを同芯位置に配置することができる。それ故、発電用水車５が回転した際の回転振動や回転ノイズの発生を確実に防止することができる。 (Main effects of this form)
As described above, in the hydroelectric generator 1 of this embodiment, when configuring the power generation water turbine 5, the cylindrical body 50 in which the blades 57 project from the outer peripheral surface, the first radial bearing 51, and the second radial bearing 52. Are formed separately, even when the cylindrical body 50, the first radial bearing 51, and the second radial bearing 52 are made of a resin molded product, sink marks or the like are unlikely to occur. Therefore, the first radial bearing 51 and the second radial bearing 52 can be manufactured by resin molding so that both the shaft holes 510 and 520 have the same size with high dimensional accuracy. In addition, after the first radial bearing 51 is fixed to the cylindrical body 50, the second radial bearing 52 is positioned with reference to the shaft hole 510 of the first radial bearing 51. Therefore, the first radial bearing 51 And the second radial bearing 52 can be arranged at a concentric position. Therefore, it is possible to reliably prevent the occurrence of rotational vibration and rotational noise when the power generation water turbine 5 rotates.

また、円筒体５０と、第１のラジアル軸受５１および第２のラジアル軸受５２とが別体であるため、円筒体第１のラジアル軸受５１および第２のラジアル軸受５２についてはカーボンファイバー含有ポリアセタール樹脂などの耐磨耗性材料で形成し、ポリフェニレンエーテルなどの安価な樹脂材料や軽量化に適した樹脂材料で円筒体５０を形成することも可能である。それ故、ラジアル軸受５１、５２を耐磨耗性材料で構成した場合でも製造コストを低く抑えることができる。   Further, since the cylindrical body 50, the first radial bearing 51, and the second radial bearing 52 are separate bodies, the carbon fiber-containing polyacetal resin is used for the first radial bearing 51 and the second radial bearing 52. It is also possible to form the cylindrical body 50 from an inexpensive resin material such as polyphenylene ether or a resin material suitable for weight reduction. Therefore, even when the radial bearings 51 and 52 are made of an abrasion resistant material, the manufacturing cost can be kept low.

また、第１のラジアル軸受５１および第２のラジアル軸受５２では、軸穴５１０、５２０を囲むように軸線方向に凹む周溝５１８、５２８が形成され、軸穴５１０、５２０と周溝５１８、５２８との間には肉薄の円筒壁５１９、５２９が形成されている。しかも、軸穴５１０、５２０のうち、支軸４との摺動部分５１１、５２１の全体が肉薄の円筒壁５１９、５２９で構成されている。このため、第１のラジアル軸受５１および第２のラジアル軸受５２を樹脂成形により製造する際、摺動部分５１１、５２１でのヒケを防止できる。それ故、第１のラジアル軸受５１および第２のラジアル軸受５２では、軸穴５１０、５２０の摺動部分５１１、５２１の径寸法に高い精度を得ることができる。また、第１のラジアル軸受５１を円筒体５０の貫通穴５０１に圧入した際に、その変形が周溝５１８で吸収されるので、軸穴５１０の内径寸法に影響を及ぼさない。さらに、第１のラジアル軸受５１および第２のラジアル軸受５２を円筒体５０の貫通穴５０１に溶着した際に、その変形が周溝５１８、５２８で吸収されるので、軸穴５１０、５２０の内径寸法に影響を及ぼさないという利点がある。   Further, in the first radial bearing 51 and the second radial bearing 52, circumferential grooves 518 and 528 that are recessed in the axial direction are formed so as to surround the shaft holes 510 and 520, and the shaft holes 510 and 520 and the circumferential grooves 518 and 528 are formed. Thin cylindrical walls 519 and 529 are formed between the two. In addition, of the shaft holes 510 and 520, the entire sliding portions 511 and 521 with the support shaft 4 are constituted by thin cylindrical walls 519 and 529. For this reason, when the 1st radial bearing 51 and the 2nd radial bearing 52 are manufactured by resin molding, the sink in the sliding parts 511 and 521 can be prevented. Therefore, in the first radial bearing 51 and the second radial bearing 52, high accuracy can be obtained in the diameter dimensions of the sliding portions 511 and 521 of the shaft holes 510 and 520. Further, when the first radial bearing 51 is press-fitted into the through hole 501 of the cylindrical body 50, the deformation is absorbed by the circumferential groove 518, so that the inner diameter dimension of the shaft hole 510 is not affected. Further, when the first radial bearing 51 and the second radial bearing 52 are welded to the through hole 501 of the cylindrical body 50, the deformation is absorbed by the circumferential grooves 518 and 528. There is an advantage that the dimensions are not affected.

また、貫通穴５０１の内周面と第２のラジアル軸受５２の外周面とのクリアランスが、貫通穴５０１の内周面と第１のラジアル軸受５１の外周面とのクリアランスより大きいため、第１のラジアル軸受５１については貫通穴５０１の一方側端部に圧入でき、第１のラジアル軸受５１の軸穴５１０を基準に第２のラジアル軸受５２の位置決めを行う際には、第２のラジアル軸受５２が貫通穴５０１の他方側端部で内周面に当たって芯出しできないという事態を回避することができる。   Further, since the clearance between the inner peripheral surface of the through hole 501 and the outer peripheral surface of the second radial bearing 52 is larger than the clearance between the inner peripheral surface of the through hole 501 and the outer peripheral surface of the first radial bearing 51, the first The radial bearing 51 can be press-fitted into one end of the through hole 501, and when the second radial bearing 52 is positioned with reference to the shaft hole 510 of the first radial bearing 51, the second radial bearing 51 is used. It is possible to avoid a situation in which 52 cannot hit the inner peripheral surface at the other side end of the through hole 501 and cannot be centered.

さらに、発電用水車５を組み立てる際の芯出し工程では、貫通穴５０１の一方側端部に固定された第１のラジアル軸受５１の軸穴５１０に位置決め軸９を嵌めた後、この位置決め軸９を第２のラジアル軸受５２の軸穴５２０に嵌めて第２のラジアル軸受５２を位置決めする。このため、第１のラジアル軸受５１の軸穴５１０を基準に第２のラジアル軸受５２の位置決めを容易にかつ、確実に行うことができる。   Further, in the centering step when assembling the power generation water turbine 5, the positioning shaft 9 is fitted into the shaft hole 510 of the first radial bearing 51 fixed to one end of the through hole 501, and then the positioning shaft 9 Is fitted into the shaft hole 520 of the second radial bearing 52 to position the second radial bearing 52. For this reason, the positioning of the second radial bearing 52 can be easily and reliably performed based on the shaft hole 510 of the first radial bearing 51.

また、本形態では、射出口３４から射出された水の一部は、上側羽根部５７１に直接、ぶつかる一方、射出口３４から射出された水の残りは、下側羽根部５７２の先端部を連結する円筒板部５８にぶつかるため、円筒板部５８は振動防止壁として機能する。すなわち、円筒板部５８にぶつかった水の圧力は、発電用水車５に調芯作用を発揮するため、発電用水車５が回転した際の回転振動や回転ノイズの発生を確実に防止することができる。   Further, in this embodiment, a part of the water ejected from the ejection port 34 directly collides with the upper blade portion 571, while the rest of the water ejected from the ejection port 34 reaches the tip portion of the lower blade portion 572. Since it hits the cylindrical plate part 58 to be connected, the cylindrical plate part 58 functions as a vibration preventing wall. That is, the pressure of the water hitting the cylindrical plate portion 58 exerts an alignment action on the power generation water turbine 5, so that it is possible to reliably prevent the generation of rotational vibration and rotation noise when the power generation water turbine 5 rotates. it can.

しかも、上側羽根部５７１に直接、ぶつかった後の水流は、円筒板部５８の内側を通る際、下側羽根部５７２に効率よくぶつかるため、発電用水車５を効率よく回転させる。従って、水力発電装置１の発電効率が高いという利点がある。   In addition, the water flow after directly hitting the upper blade portion 571 efficiently hits the lower blade portion 572 when passing through the inside of the cylindrical plate portion 58, so that the power generation turbine 5 is efficiently rotated. Therefore, there is an advantage that the power generation efficiency of the hydroelectric generator 1 is high.

また、本形態では、射出口３４および羽根５７は等角度間隔に複数、形成されているため、安定した発電を行うことができる。しかも、本形態では、射出口３４は等角度間隔に４つ形成されている一方、羽根５７は等角度間隔に７枚形成されており、射出口３４の数と、羽根５７の枚数とは、互いに素の関係にあるため、一方が他方の整数倍となる条件を避けてある。このため、射出口３４から射出される水が２枚以上の羽根５７に同時に強烈に当たることを防ぐことができるので、発電用水車５に大きな力が同時に加わることを防止できる。それ故、発電用水車５が回転した際の回転振動や回転ノイズの発生を確実に防止することができる。すなわち、射出口３４の数と、羽根５７の枚数との間で一方が他方の整数倍となる条件であると、射出口３４から射出される水が複数枚の羽根５７に同時に強烈に当たるため、発電用水車５に大きな力が同時に加わって回転振動や回転ノイズが発生しやすくなるが、本形態によれば、かかる現象の発生を回避することができる。   Further, in this embodiment, since a plurality of the injection ports 34 and the blades 57 are formed at equiangular intervals, stable power generation can be performed. Moreover, in this embodiment, four injection ports 34 are formed at equal angular intervals, while seven blades 57 are formed at equal angular intervals. The number of injection ports 34 and the number of blades 57 are as follows: Since they are in a relatively prime relationship, a condition in which one is an integer multiple of the other is avoided. For this reason, since it can prevent that the water inject | emitted from the injection port 34 hits two or more blade | wings 57 simultaneously simultaneously, it can prevent that big force is simultaneously added to the water turbine 5 for electric power generation. Therefore, it is possible to reliably prevent the occurrence of rotational vibration and rotational noise when the power generation water turbine 5 rotates. That is, when one of the number of ejection ports 34 and the number of blades 57 is a multiple of the other, the water ejected from the ejection port 34 strikes a plurality of blades 57 simultaneously and strongly. Although a large force is simultaneously applied to the power generation water turbine 5 to easily generate rotational vibration and rotational noise, the occurrence of such a phenomenon can be avoided according to this embodiment.

［その他の実施の形態］
上記形態においては、発電用水車５を組み立てる際、円筒体５０に対して第１のラジアル軸受５１および第２のラジアル軸受５２を溶着により固定したが、機械的な潰しや接着などの方法を採用してもよい。また、上記形態では、射出口３４の数と羽根５７の枚数が互いに素の関係にあったが、一方が他方の整数倍となる条件に設定した場合に本発明を適用してもよい。 [Other embodiments]
In the above embodiment, when assembling the power generation water turbine 5, the first radial bearing 51 and the second radial bearing 52 are fixed to the cylindrical body 50 by welding, but a method such as mechanical crushing or adhesion is adopted. May be. Moreover, in the said form, although the number of the injection ports 34 and the number of the blade | wings 57 had the prime relationship, you may apply this invention, when it sets to the conditions used as one integer multiple of the other.

（ａ）、（ｂ）は、本発明を適用した水力発電装置の平面図、およびＡ−Ａ′断面図である。(A), (b) is a top view and AA 'sectional view of a hydroelectric generator to which the present invention is applied. （ａ）、（ｂ）、（ｃ）は、図１に示す水力発電装置に用いた発電用水車を第１のラジアル軸受側からみたときの斜視図、この発電用水車を第２のラジアル軸受側からみたときの平面図、およびＢ−Ｂ′断面図である。(A), (b), (c) is a perspective view when the water turbine for power generation used in the hydroelectric generator shown in FIG. 1 is viewed from the first radial bearing side, and the power turbine for power generation is a second radial bearing. It is the top view when seen from the side, and BB 'sectional drawing. （ａ）〜（ｄ）は、図２に示す発電用水車の組み立て方法を示す工程断面図である。(A)-(d) is process sectional drawing which shows the assembly method of the water turbine for electric power generation shown in FIG.

符号の説明Explanation of symbols

１ 水力発電装置
５ 発電用水車
６ ステータ部
９ 位置決め軸
３４ 射出口
３５ 水車室
５０ 円筒体
５１ 第１のラジアル軸受
５２ 第２のラジアル軸受
５５ 永久磁石
５７ 羽根
５８ 円筒板部
５０１ 貫通穴
５１０、５２０ 軸穴
５１８、５２８ 周溝
５７１ 上側羽根部
５７２ 下側羽根部 DESCRIPTION OF SYMBOLS 1 Hydroelectric generator 5 Power generation turbine 6 Stator part 9 Positioning shaft 34 Injection port 35 Water wheel chamber 50 Cylinder body 51 First radial bearing 52 Second radial bearing 55 Permanent magnet 57 Blade 58 Cylindrical plate part 501 Through hole 510, 520 Shaft holes 518, 528 Circumferential groove 571 Upper blade portion 572 Lower blade portion

Claims (6)

流体入口から流体出口に到る流路と、該流路の途中位置に配置された支軸と、該支軸に回転可能に支持された円筒状の発電用水車とを有する水力発電装置において、
前記発電用水車は、外周面から羽根が張り出す樹脂成形品からなる円筒体と、該円筒体と別体に構成され、前記支軸が貫通する軸穴をもって前記円筒体の貫通穴の一方側端部に固定された円筒状の第１のラジアル軸受と、前記円筒体と別体に構成され、前記支軸が貫通する軸穴をもって前記貫通穴の他方側端部に固定された円筒状の第２のラジアル軸受とを備え、
前記円筒体は、前記支軸の軸線方向において前記第１のラジアル軸受が位置する側に、前記軸線方向において前記第２のラジアル軸受が位置する側で筒状の永久磁石が外周に固着された上半部より大径かつ肉厚の下端部を備えており、
当該下端部の外周に前記羽根が形成され、
前記第１のラジアル軸受は、樹脂製ラジアル軸受であって、当該樹脂製ラジアル軸受では、前記軸穴を囲むように軸線方向に凹む周溝が形成され、前記軸穴と前記周溝との間には肉薄の円筒壁が構成されており、
当該第１のラジアル軸受は、前記貫通穴内部のうち、前記下端部に対して半径方向内側に位置する部分に固定されていることを特徴とする水力発電装置。 In a hydroelectric generator having a flow path from a fluid inlet to a fluid outlet, a support shaft disposed in the middle of the flow path, and a cylindrical power generation turbine rotatably supported by the support shaft,
The water turbine for power generation is configured separately from the cylindrical body made of a resin molded product with blades extending from the outer peripheral surface, and has a shaft hole through which the support shaft passes. One side of the through hole of the cylindrical body A cylindrical first radial bearing fixed to an end, and a cylindrical body configured separately from the cylindrical body and having a shaft hole through which the support shaft passes are fixed to the other end of the through hole. e Bei a second radial bearing,
In the cylindrical body, a cylindrical permanent magnet is fixed to the outer periphery on the side where the first radial bearing is located in the axial direction of the support shaft and on the side where the second radial bearing is located in the axial direction. It has a lower end that is larger in diameter and thicker than the upper half,
The blade is formed on the outer periphery of the lower end,
The first radial bearing is a resin radial bearing, and in the resin radial bearing, a circumferential groove that is recessed in an axial direction is formed so as to surround the shaft hole, and the first radial bearing is formed between the shaft hole and the circumferential groove. Has a thin cylindrical wall,
The said 1st radial bearing is being fixed to the part located inside a radial direction with respect to the said lower end part among the said through-holes, The hydroelectric generator characterized by the above-mentioned. 請求項１において、前記第２のラジアル軸受は、樹脂製ラジアル軸受であって、当該樹脂製ラジアル軸受では、前記軸穴を囲むように軸線方向に凹む周溝が形成され、前記軸穴と前記周溝との間には肉薄の円筒壁が構成されていることを特徴とする水力発電装置。 According to claim 1, wherein the second radial bearing, I resinous radial bearing der, in the resin-made radial bearing, the circumferential groove which is recessed in the axial direction so as to surround the shaft hole is formed, and the shaft hole A thin-walled cylindrical wall is formed between the circumferential grooves. 請求項２において、前記第１のラジアル軸受を構成する前記樹脂製ラジアル軸受、および前記第２のラジアル軸受を構成する前記樹脂製ラジアル軸受のいずれにおいても、前記支軸との摺動部分の全体が前記円筒壁で構成されていることを特徴とする水力発電装置。 3. The entire sliding portion of the support shaft according to claim 2, wherein the resin radial bearing constituting the first radial bearing and the resin radial bearing constituting the second radial bearing are both. Is constituted by the cylindrical wall. 請求項１ないし３のいずれかにおいて、前記貫通穴の他方側端部における内周面と前記第２のラジアル軸受の外周面とのクリアランスが、前記貫通穴の一方側端部における内周面と前記第１のラジアル軸受の外周面とのクリアランスより大きいことを特徴とする水力発電装置。 In any one of claims 1 to 3, the clearance between the inner peripheral surface and the outer peripheral surface of said second radial bearing at the other end of the through hole, the inner peripheral surface at the one side end portion of the through hole A hydroelectric generator having a larger clearance from the outer peripheral surface of the first radial bearing. 請求項１ないし４の何れか一項に記載の水力発電装置の製造方法において、
前記第１のラジアル軸受および前記第２のラジアル軸受を前記円筒体に取り付けるにあたっては、
前記円筒体の前記貫通穴の一方側端部に前記第１のラジアル軸受を固定する第１のラジアル軸受固定工程と、当該第１のラジアル軸受の軸穴を基準に前記第２のラジアル軸受を前記貫通穴の他方側端部で位置決めする芯出し工程と、前記第２のラジアル軸受を前記貫通穴の他方側端部に固定する第２のラジアル軸受固定工程とを行うことを特徴とする水力発電装置の製造方法。 In the manufacturing method of the hydroelectric generator according to any one of claims 1 to 4,
In attaching the first radial bearing and the second radial bearing to the cylindrical body,
A first radial bearing fixation step for fixing the first radial bearing to one side end portion of said through hole of said cylindrical body, said relative to the shaft hole of the first radial bearing second radial bearing A hydraulic power characterized by performing a centering step of positioning at the other end portion of the through hole and a second radial bearing fixing step of fixing the second radial bearing to the other end portion of the through hole. A method for manufacturing a power generator. 請求項５において、前記芯出し工程では、前記貫通穴の一方側端部に固定された前記第１のラジアル軸受の軸穴に位置決め軸を嵌めた後、当該位置決め軸を前記第２のラジアル軸受の軸穴に嵌めて当該第２のラジアル軸受を前記貫通穴の他方側端部で位置決めすることを特徴とする水力発電装置の製造方法。   6. The centering step according to claim 5, wherein a positioning shaft is fitted into a shaft hole of the first radial bearing fixed to one end of the through hole, and then the positioning shaft is used as the second radial bearing. A method of manufacturing a hydroelectric power generator, wherein the second radial bearing is positioned at the other end of the through hole by being fitted in the shaft hole.
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CN2007100896372A CN101046186B (en) 2006-03-27 2007-03-21 Hydraulic power generating device and manufacturing method therefor
CN2011100372231A CN102094745B (en) 2006-03-27 2007-03-21 Hydraulic power generating device and manufacturing method therefor
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