JPH0587037A - Variable pitch propeller driving device - Google Patents
Variable pitch propeller driving deviceInfo
- Publication number
- JPH0587037A JPH0587037A JP3251339A JP25133991A JPH0587037A JP H0587037 A JPH0587037 A JP H0587037A JP 3251339 A JP3251339 A JP 3251339A JP 25133991 A JP25133991 A JP 25133991A JP H0587037 A JPH0587037 A JP H0587037A
- Authority
- JP
- Japan
- Prior art keywords
- gear
- shaft
- main shaft
- output shaft
- variable pitch
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Granted
Links
Classifications
-
- 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
Landscapes
- Hydraulic Turbines (AREA)
- Structure Of Transmissions (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明は、水力機械等における可
変ピッチプロペラの回転主軸に対する羽根の取付角を変
化させるための駆動装置に関する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a drive device for changing a mounting angle of blades with respect to a rotating main shaft of a variable pitch propeller in a hydraulic machine or the like.
【０００２】[0002]
【従来の技術】一般に、水車やポンプ或いはブロワ等に
おいては、回転軸に対する羽根の取付角度を任意に変更
できる可変ピッチプロペラを使用し、その羽根の取付角
を変化させることによってその負荷の調節を行うことが
できるようにしたものがある。2. Description of the Related Art Generally, in a water turbine, a pump, a blower or the like, a variable pitch propeller capable of arbitrarily changing a mounting angle of a blade with respect to a rotating shaft is used and its load is adjusted by changing a mounting angle of the blade. There are things that you can do.
【０００３】すなわち、回転主軸の一端に、複数の羽根
を放射状に装着したランナボスが一体的に連結してあ
り、上記各羽根の支持軸が上記ランナボス内において軸
線周りに回動自在に軸支してある。一方、中空状に形成
された回転主軸の一部には油圧シリンダが形成され、そ
の油圧シリンダ内に配設されたピストンに、中空の回転
主軸内に同心的に挿通された操作ロッドの一端が連結さ
れ、その他端がリンク機構を介して前記各羽根の支持軸
に連結されている。That is, a runner boss having a plurality of blades mounted radially is integrally connected to one end of the rotary main shaft, and the support shafts of the respective blades are rotatably supported around the axis in the runner boss. There is. On the other hand, a hydraulic cylinder is formed in a part of the hollow rotating main shaft, and one end of an operating rod concentrically inserted in the hollow rotating main shaft is inserted into a piston arranged in the hydraulic cylinder. The blades are connected and the other end is connected to the support shaft of each blade via a link mechanism.
【０００４】そして、回転主軸の端部から配圧弁を介し
て圧油を上記油圧シリンダに供給し、ピストンを任意の
方向に移動させることによって、前記操作ロッドを軸線
方向に移動させ、その移動によって羽根の各支持軸を軸
線回りに回動させ、各羽根の取付角度を変化させるよう
にしてある。Then, pressure oil is supplied to the hydraulic cylinder from the end of the rotary main shaft through a pressure distribution valve, and the piston is moved in an arbitrary direction to move the operating rod in the axial direction. Each support shaft of the blade is rotated around the axis to change the mounting angle of each blade.
【０００５】[0005]
【発明が解決しようとする課題】ところが、このような
装置においては、回転主軸の駆動回転中にも羽根の取付
角度の調整を行うことができるようにするため、油圧シ
リンダに対する油圧の給排を回転シール機構等を介して
行わなければならず、油圧のシール機構が複雑となる等
の問題がある。特に、水車等のような空気よりも粘性抵
抗が大きい流体を扱うものでは、羽根に対する抵抗が大
きな反力となって油圧シリンダ側に負荷するため、相当
な高圧の油圧を作動させなければならず、シール部での
油洩れ焼付き等の事故が発生する可能性もある。However, in such a device, the supply and discharge of the hydraulic pressure to and from the hydraulic cylinder is performed in order to adjust the mounting angle of the blades even during the drive rotation of the rotary main shaft. This has to be done via a rotary seal mechanism or the like, and there is a problem that the hydraulic seal mechanism becomes complicated. In particular, in the case of a fluid such as a water wheel that handles a fluid having a larger viscous resistance than air, the resistance against the blades becomes a large reaction force and loads the hydraulic cylinder side, so that a considerably high hydraulic pressure must be operated. There is also a possibility of accidents such as oil leakage and seizure at the seal.
【０００６】一方、油圧シリンダの代わりに電動機を使
用し、この電動機の出力軸を前記操作ロッドに螺合させ
て、その操作ロッドを往復動させるようにしたものも提
案されている。しかし、このような場合、電動機の回転
軸と回転主軸との間に相対回転差を発生させることによ
り操作ロッドを駆動するとともに、通常はこの電動機の
回転軸と回転主軸とを一体回転させ羽根の取付角度が変
わらないようにする必要があるが、従来のものでは必ず
しもその作動が確実に行われない等の問題がある。On the other hand, it has been proposed that an electric motor is used instead of the hydraulic cylinder, and the output shaft of the electric motor is screwed onto the operating rod so that the operating rod reciprocates. However, in such a case, the operating rod is driven by generating a relative rotation difference between the rotating shaft of the electric motor and the rotating main shaft, and normally the rotating shaft and the rotating main shaft of the electric motor are integrally rotated to rotate the blade. It is necessary to prevent the mounting angle from changing, but there is a problem in that the operation is not always performed with the conventional one.
【０００７】本発明はこのような点に鑑み、油圧シリン
ダを使用する必要がなく、確実に羽根の取付角度を調節
し得る可変ピッチプロペラ駆動装置を得ることを目的と
する。SUMMARY OF THE INVENTION In view of the above points, an object of the present invention is to provide a variable pitch propeller drive device which can adjust the blade mounting angle without using a hydraulic cylinder.
【０００８】[0008]
【課題を解決するための手段】本発明は、回転主軸と同
心状に配設された出力軸を相対的に回転させることによ
り、回転主軸に取付けられた可変ピッチ羽根の取付角度
を変化させる可変ピッチプロペラ駆動装置において、入
力軸を介して電動機に連結された太陽歯車と、この太陽
歯車と噛合し自転しながら上記太陽歯車の外周を公転す
る遊星歯車と、この遊星歯車と噛合する第３の歯車から
なる歯車列を有し、上記遊星歯車又は第３の歯車のいず
れか一方の歯車を前記出力軸に連結するとともに、他方
の歯車を固定軸と前記回転主軸との間に介装された変速
装置によって駆動し、前記太陽歯車が停止していると
き、前記出力軸と回転主軸との回転速度が等しくなるよ
うに各変速比を選定したことを特徴とする。SUMMARY OF THE INVENTION According to the present invention, a variable pitch vane mounted on a rotary main shaft is changed by rotating an output shaft concentric with the rotary main shaft. In a pitch propeller drive device, a sun gear connected to an electric motor via an input shaft, a planetary gear that revolves around the outer periphery of the sun gear while rotating with the sun gear and a third gear that meshes with the planetary gear. A gear train composed of gears, wherein either the planetary gear or the third gear is connected to the output shaft, and the other gear is interposed between the fixed shaft and the rotary main shaft. Each gear ratio is selected such that the output shaft and the rotating main shaft have the same rotational speed when driven by a transmission and the sun gear is stopped.
【０００９】[0009]
【作用】電動機が不作動状態とされて入力軸を介して太
陽歯車が固定状態にある場合には、変速装置を介して回
転主軸の回転が、遊星歯車又は第３の歯車の一方の歯車
に伝達され、その歯車によって出力軸が上記回転主軸と
同一速度で回転され、回転主軸に取付けられた羽根の取
付角度が所定値に維持される。そこで、電動機と駆動し
て太陽歯車を回転させると、上記一方の歯車の回転速度
が変り、その一方の歯車により回転される出力軸と前記
回転主軸との間の相対的回転速度が変り、その回転主軸
と出力軸との相対的回転速度の違いによって操作ロッド
が駆動され、その操作ロッドを介して上記羽根の取付角
度が変更される。When the electric motor is deactivated and the sun gear is fixed via the input shaft, the rotation of the rotating main shaft is transmitted to one of the planetary gear or the third gear via the transmission. The output shaft is transmitted by the gear and the output shaft is rotated at the same speed as the rotating main shaft, and the mounting angle of the blades mounted on the rotating main shaft is maintained at a predetermined value. Therefore, when the sun gear is rotated by driving with an electric motor, the rotation speed of the one gear changes, and the relative rotation speed between the output shaft and the rotation main shaft rotated by the one gear changes, The operating rod is driven by the difference in relative rotational speed between the rotating main shaft and the output shaft, and the mounting angle of the blade is changed via the operating rod.
【００１０】[0010]
【実施例】以下、添付図面を参照して本発明の実施例に
ついて説明する。Embodiments of the present invention will be described below with reference to the accompanying drawings.
【００１１】図２は、本発明の装置を適用した可変ピッ
チプロペラ水車の概略構成を示す図であって、下端にラ
ンナボス１ａを一体的に装着した回転主軸１が軸受２に
よって回転自在に支持されている。上記ランナボス１ａ
には放射方向に複数の羽根３が取付けられており、その
各羽根の支持軸３ａがランナボス１ａ内で軸支され、支
持軸３ａを回動させることによって羽根３の取付角度を
変化させることができるようにしてある。FIG. 2 is a diagram showing a schematic structure of a variable pitch propeller turbine to which the device of the present invention is applied. A rotary main shaft 1 integrally attached with a runner boss 1a at its lower end is rotatably supported by a bearing 2. ing. Above runner boss 1a
A plurality of blades 3 are attached in the radial direction, the support shafts 3a of the respective blades are rotatably supported in the runner boss 1a, and the attachment angle of the blades 3 can be changed by rotating the support shafts 3a. I am able to do it.
【００１２】一方、回転主軸１は中空状に形成され、こ
の回転主軸１内に操作ロッド４が軸線方向にのみ移動可
能に同心状に配設され、その操作ロッド４の下端に固着
されたアーム４ａが、リンク及びレバー機構５を介して
前記羽根３の各支持軸３ａに連結されている。したがっ
て、上記操作ロッド４を軸線方向に往復移動させること
によって、リンク及びレバー機構５を介して各羽根３の
取付角度を変化させることができる。On the other hand, the rotating main shaft 1 is formed in a hollow shape, and an operating rod 4 is concentrically arranged in the rotating main shaft 1 so as to be movable only in the axial direction, and an arm fixed to the lower end of the operating rod 4. 4a is connected to each support shaft 3a of the blade 3 via a link and lever mechanism 5. Therefore, by reciprocally moving the operation rod 4 in the axial direction, the attachment angle of each blade 3 can be changed via the link and lever mechanism 5.
【００１３】上記回転主軸１の頂端部には、本発明に係
る可変ピッチプロペラ駆動装置の作動機構６が装着され
ており、その作動機構６への入力軸７がカップリング８
及び中間軸９を介して電動機１０に連結されている。ま
た、上記作動機構６の他端にある出力軸１１は推力軸受
１４により大きな推力を支えるようになっており、その
下端に形成されたねじ部１１ａが前記操作ロッド４の頂
部４ｂに螺合されている。An operating mechanism 6 of the variable pitch propeller drive device according to the present invention is mounted on the top end of the rotary main shaft 1, and an input shaft 7 to the operating mechanism 6 is coupled with a coupling 8.
And, it is connected to the electric motor 10 via the intermediate shaft 9. The output shaft 11 at the other end of the operating mechanism 6 is designed to support a large thrust by a thrust bearing 14, and a screw portion 11a formed at the lower end of the output shaft 11 is screwed to the top portion 4b of the operation rod 4. ing.
【００１４】したがって、回転主軸１と出力軸１１との
間に相対的な回転を発生させると、操作ロッド４が軸線
方向に移動し、リンク及びレバー機構５を介して各羽根
３の取付け角度が変化される。また、回転主軸１と出力
軸１１とを一体回転させると、出力軸１１と操作ロッド
４が一体的に回転するので、操作ロッド４の軸線方向の
移動がなく、各羽根３の取付角度は所定値に維持され
る。Therefore, when a relative rotation is generated between the rotating main shaft 1 and the output shaft 11, the operating rod 4 moves in the axial direction, and the mounting angle of each blade 3 is changed via the link and lever mechanism 5. Be changed. Further, when the rotating main shaft 1 and the output shaft 11 are integrally rotated, the output shaft 11 and the operating rod 4 rotate integrally, so that the operating rod 4 does not move in the axial direction, and the mounting angle of each blade 3 is predetermined. Maintained at the value.
【００１５】図１は、上記作動機構６部の一実施例を示
す図であって、その作動機構６のケース１５が前記回転
主軸１の頂部に一体的に装着されている。そのケース１
５の頂壁には固定軸１６が貫挿され、軸受１６ａにより
相対的回転可能に装着されており、その固定軸１６は図
２に示すようにアーム１７及びストッパー１８によって
その回転運動が拘束されている。FIG. 1 is a view showing an embodiment of the above-mentioned operating mechanism 6 part, in which a case 15 of the operating mechanism 6 is integrally mounted on the top of the rotary spindle 1. Case 1
A fixed shaft 16 is inserted through the top wall of the bearing 5 and is rotatably mounted by a bearing 16a. The fixed shaft 16 has its rotational movement restricted by an arm 17 and a stopper 18 as shown in FIG. ing.
【００１６】上記固定軸１６には前記入力軸７が同心的
に貫挿され、固定軸１６と入力軸７との間に設けられて
いる軸受１９及び後述するアームに設けられた軸支部２
０により回動自在に支持されている。そして、この入力
軸７の下部には太陽歯車２１が一体的に形成されてお
り、この太陽歯車２１には太陽歯車２１を中心として公
転する複数個の遊星歯車２２が噛合されている。The input shaft 7 is concentrically inserted through the fixed shaft 16, and a bearing 19 provided between the fixed shaft 16 and the input shaft 7 and a shaft support portion 2 provided on an arm to be described later are provided.
It is rotatably supported by 0. A sun gear 21 is integrally formed on the lower portion of the input shaft 7, and a plurality of planet gears 22 that revolve around the sun gear 21 are meshed with the sun gear 21.
【００１７】遊星歯車２２は、出力軸１１と一体に形成
されたアーム１２に設けられた支持軸２３に対して回転
自在に装着されており、太陽歯車２１の周囲を自転しな
がら公転し、出力軸１１の回転を行なう。さらに、上記
遊星歯車２２の外周には内歯歯車２４が配設されてお
り、その内歯歯車２４の第１の歯車２４ａが上記遊星歯
車２２に噛合されている。また、上記出力軸１１は入力
軸７と同一軸線上に配設され、ケース１５の底壁を貫通
するとともに、軸受２５ａ、２５ｂによってそのケース
１５に回転自在に軸受されている。The planetary gear 22 is rotatably mounted on a support shaft 23 provided on an arm 12 formed integrally with the output shaft 11, and revolves around the sun gear 21 while revolving around the sun gear 21 to output. The shaft 11 is rotated. Further, an internal gear 24 is arranged on the outer periphery of the planetary gear 22, and a first gear 24 a of the internal gear 24 is meshed with the planetary gear 22. The output shaft 11 is arranged on the same axis as the input shaft 7, penetrates the bottom wall of the case 15, and is rotatably supported by the case 15 by bearings 25a and 25b.
【００１８】一方、ケース１５内に挿入され軸受１６ａ
によってケース１５に軸支された固定軸１６の下端に
は、第２の太陽歯車２６が一体的に形成されており、こ
の太陽歯車２６の外周にはこの太陽歯車２６を中心とし
て公転する複数個の遊星歯車２７が噛合されており、こ
の遊星歯車２７にはその外周に配設された内歯歯車２４
の第２の歯車２４ｂに噛合されている。On the other hand, the bearing 16a inserted into the case 15
A second sun gear 26 is integrally formed on the lower end of a fixed shaft 16 pivotally supported by the case 15, and a plurality of sun gears 26 revolve around the sun gear 26 on the outer periphery thereof. The planetary gears 27 are meshed with each other, and the planetary gears 27 have internal gears 24 arranged on the outer periphery thereof.
Is meshed with the second gear 24b.
【００１９】また、上記遊星歯車２７は、ケース１５の
内壁に固定されたアーム２８から突設された軸２９に回
転自在に装着されている。さらにケース１５と固定軸１
６及び出力軸１１間、及び固定軸１６と入力軸７間には
それぞれパッキング３０ａ、３０ｂ、３０ｃが設けら
れ、上記ケース１５内には潤滑油が充填されている。The planetary gear 27 is rotatably mounted on a shaft 29 projecting from an arm 28 fixed to the inner wall of the case 15. Further, the case 15 and the fixed shaft 1
Packings 30a, 30b and 30c are provided between the shaft 6 and the output shaft 11 and between the fixed shaft 16 and the input shaft 7, respectively, and the case 15 is filled with lubricating oil.
【００２０】そこで、２組の歯車の太陽歯車２１と２６
の歯数をそれぞれＺ1 及びＺ1 ′内歯歯車２４の第１及
び第２の歯車２４ａ、２４ｂをＺ2 及びＺ2 ′し、２組
の歯車の歯数比をＺ1 ／Ｚ2 ＝Ｚ1 ′／Ｚ2 ′＝／１／
Ｒのように等しくする。Therefore, the two sets of sun gears 21 and 26 are set.
The number of teeth of Z 1 and Z 1 ′ is Z 2 and Z 2 ′ of the first and second gears 24a and 24b of the internal gear 24, respectively, and the tooth number ratio of the two sets of gears is Z 1 / Z 2 = Z 1 ′ / Z 2 ′ ＝ / 1 /
Make equal like R.
【００２１】しかして、回転主軸１がω0 の速度で回転
しており、電動機１０が停止設定され太陽歯車２１が停
止している場合には、太陽歯車２６が固定転１６の回転
拘束により固定状態であるので、遊星歯車２７がケース
１５及びアーム２８を介して回転主軸１から駆動され、
公転軌跡上をω0 の速度で公転し、その回転力によって
第２の歯車２４ｂを介して内歯歯車２４がω1 の速度で
回転主軸１と同一方向に回転駆動される（図３）。However, when the rotating main shaft 1 is rotating at a speed of ω 0 , the electric motor 10 is set to be stopped, and the sun gear 21 is stopped, the sun gear 26 is fixed by the rotation restraint of the fixed roller 16. Since it is in the state, the planetary gear 27 is driven from the rotary main shaft 1 via the case 15 and the arm 28,
It revolves on the revolution locus at a speed of ω 0 , and its rotational force drives the internal gear 24 to rotate in the same direction as the rotation main shaft 1 at a speed of ω 1 via the second gear 24b (FIG. 3).
【００２２】一方、上述のように内歯歯車２４がω1 の
速度で回転すると、太陽歯車２１が停止しているので、
遊星歯車２２が歯車２４ａを介して太陽歯車２１の回り
に自転しながらω0 ′の速度で公転させられ、その遊星
歯車２２の公転によってアーム１２を介して出力軸１１
がω0 ′の速度で回転させられる（図４）。On the other hand, when the internal gear 24 rotates at the speed of ω 1 as described above, the sun gear 21 is stopped,
The planetary gear 22 revolves around the sun gear 21 via the gear 24a while revolving at a speed of ω 0 ′, and the revolution of the planetary gear 22 causes the output shaft 11 via the arm 12 to rotate.
Are rotated at a speed of ω 0 ′ (FIG. 4).
【００２３】ところで、回転主軸１の回転速度即ち遊星
歯車２７の公転速度ω0 と内歯歯車２４の回転速度ω1
との間には、次の関係がある。By the way, the rotational speed of the rotary main shaft 1, that is, the revolution speed ω 0 of the planetary gear 27 and the rotational speed ω 1 of the internal gear 24.
Has the following relationship.
【００２４】ω1 ＝（１＋Ｚ1 ′／Ｚ2 ′）ω0 また、内歯歯車２４の回転速度ω1 と出力軸１１即ち遊
星歯車２２の公転速度ω0 ′の間にも次の関係がある ω1 ＝（１−Ｚ1 ′／Ｚ2 ′）ω0 ′ 一方、歯車数には前述のようにＺ1 ／Ｚ2 ＝Ｚ1 ′／Ｚ
2 ′＝１／Ｒと等しくしてあるので、ω0 ＝ω0 ′とな
り、出力軸１１は回転主軸１と一体の如く同調回転する
ことになる。そのため、操作ロッド４と出力軸１１とが
一体的に回転して操作ロッド４が軸線方向に移動される
ことがなく、羽根３の取付角度は所定値に維持される。Ω 1 = (1 + Z 1 ′ / Z 2 ′) ω 0 Further , the following relationship is also present between the rotational speed ω 1 of the internal gear 24 and the revolution speed ω 0 ′ of the output shaft 11, that is, the planetary gear 22. Ω 1 = (1-Z 1 ′ / Z 2 ′) ω 0 ′ On the other hand, the number of gears is Z 1 / Z 2 = Z 1 ′ / Z as described above.
Since it is equal to 2 '= 1 / R, ω 0 = ω 0 ′, and the output shaft 11 rotates synchronously with the rotary main shaft 1 as one body. Therefore, the operating rod 4 and the output shaft 11 do not rotate integrally to move the operating rod 4 in the axial direction, and the attachment angle of the blade 3 is maintained at a predetermined value.
【００２５】このように電動機の停止設定によって入力
軸７を停止しているときは羽根３の取付角度が変ること
はないが、入力軸７を±ωの速度で操作すると、出力軸
１１と回転主軸１すなわち操作ロッド４との間に±（１
／１＋Ｒ）ωに減速された速度差を生ずる。したがっ
て、この速度差によって操作ロッド４が上下させられ、
羽根３の取付角度が変更される。Although the mounting angle of the blades 3 does not change when the input shaft 7 is stopped by the stop setting of the electric motor as described above, when the input shaft 7 is operated at a speed of ± ω, it rotates with the output shaft 11. ± (1
/ 1 + R) ω to produce a decelerated speed difference. Therefore, the operating rod 4 is moved up and down by this speed difference,
The mounting angle of the blade 3 is changed.
【００２６】図５は、本発明の他の実施例を示す図であ
り、入力軸７の下端には傘歯車３１が装着されており、
この傘歯車３１には、自転しながら入力軸７の軸線回り
に公転する遊星傘歯車３２が噛合されている。さらにこ
の遊星傘歯車３２には上記入力軸７と同一軸線上に配設
された出力軸１１の頂端に設けられ傘歯車３１と同一歯
数を有する傘歯車３３が噛合されている。FIG. 5 is a view showing another embodiment of the present invention, in which a bevel gear 31 is attached to the lower end of the input shaft 7,
A planet bevel gear 32, which revolves around the axis of the input shaft 7 while rotating on its axis, is meshed with the bevel gear 31. Further, the planetary bevel gear 32 is meshed with a bevel gear 33 having the same number of teeth as the bevel gear 31 provided at the top end of the output shaft 11 arranged on the same axis as the input shaft 7.
【００２７】上記遊星傘歯車３２を軸支する枠体３４は
入出力軸７、１１の軸線上で回動可能にケース１５に軸
受３４ａ、３４ｂによって軸支されている。The frame 34 which supports the planetary bevel gear 32 is rotatably supported on the case 15 by bearings 34a and 34b so as to be rotatable on the axes of the input and output shafts 7 and 11.
【００２８】一方、固定軸１６の下端及び枠体３４の頂
端にはそれぞれ平歯車３５、３６が一体的に形成されて
おり、両歯車３５、３６にはそれぞれ複数の平歯車３
７、３８が噛合されている。この各平歯車３７及び３８
はともに同一軸３９に固着されており、この軸３９はケ
ース１５の内壁から突設された支持腕４０ａ、４０ｂに
回動可能に軸支されている。その他の構成は図２に示し
たものと同じである。On the other hand, spur gears 35 and 36 are integrally formed at the lower end of the fixed shaft 16 and the top end of the frame 34, respectively.
7, 38 are meshed. These spur gears 37 and 38
Are fixed to the same shaft 39, and the shaft 39 is rotatably supported by support arms 40a and 40b projecting from the inner wall of the case 15. Other configurations are the same as those shown in FIG.
【００２９】しかして、回転主軸１とともにケース１５
が回動すると、平歯車３７が平歯車３５の回りに公転し
ながら自転し、それに伴なって平歯車３８も公転しなが
ら自転してその回転力によって平歯車３６とともに枠体
３４が回転させられる。そこで、上記平歯車３５、３
７、３８、３６の歯数を順次Ｚ1 、Ｚ2 、Ｚ3 、Ｚ4 、
としたとき、歯数比が Ｚ1 ／Ｚ2 ×Ｚ3 ／Ｚ4 ＝１／Ｒ＝１／２ となるように選定されている。Then, the case 15 together with the rotary spindle 1
When is rotated, the spur gear 37 revolves around the spur gear 35 while revolving, and the spur gear 38 also revolves around the spur gear 35, so that the rotational force rotates the frame 34 together with the spur gear 36. .. Therefore, the spur gears 35, 3 are
The numbers of teeth of 7, 38, 36 are sequentially Z 1 , Z 2 , Z 3 , Z 4 ,
Then, the tooth number ratio is selected to be Z 1 / Z 2 × Z 3 / Z 4 = 1 / R = 1/2.
【００３０】したがって、上記歯車列の減速比は１−１
／Ｒとなるので、枠体３４は回転主軸１の回転方向に１
／２の速度で駆動される。Therefore, the reduction ratio of the gear train is 1-1.
/ R, so that the frame 34 is 1 in the rotation direction of the rotary spindle 1.
It is driven at a speed of / 2.
【００３１】このようにして枠体３４が回転していると
き、入力軸７を停止させ傘歯車３１を固定状態にする
と、遊星傘歯車３２が傘歯車３１の回りに公転しながら
自転し、その回転力によって傘歯車３３が回転され出力
軸１１が回転させられる。When the input shaft 7 is stopped and the bevel gear 31 is fixed while the frame 34 is thus rotating, the planet bevel gear 32 revolves around the bevel gear 31 while revolving around it. The bevel gear 33 is rotated by the rotational force and the output shaft 11 is rotated.
【００３２】ところで、傘歯車３１と傘歯車３３の歯数
が互いに同数としてあるため、出力軸１１は枠体３４と
同一方向にその２倍に増速されて回転し、結局出力軸１
１は回転主軸１と同じ速度で同一方向に回転され、操作
ロッド４の作動は行なわれない。By the way, since the bevel gear 31 and the bevel gear 33 have the same number of teeth, the output shaft 11 rotates in the same direction as the frame 34 at a speed that is twice as fast as that of the frame 34.
1 is rotated at the same speed as the rotating main shaft 1 in the same direction, and the operation rod 4 is not operated.
【００３３】一方、入力軸７を作動させると、その入力
と等速で方向反対の出力が出力軸１１に得られ、その出
力軸１１と回転主軸１との回転差に対応して操作ロッド
４が上下動され、羽根の取付角度の調整が行なわれる。On the other hand, when the input shaft 7 is actuated, an output having a constant velocity and a direction opposite to that of the input shaft 7 is obtained at the output shaft 11, and the operating rod 4 corresponds to the difference in rotation between the output shaft 11 and the rotary spindle 1. Is moved up and down, and the blade mounting angle is adjusted.
【００３４】尚、上記第１、第２の実施例においては、
共に出力軸１１と回転主軸１との回転差を一旦直線運動
に変換し、この直線運動により羽根の取付角度を変化さ
せているが、本発明はこのような例に限定されるもので
はなく、出力軸の回転により直接羽根の取付角度を変化
させても良い。例えば、本発明を通常操作軸の回転によ
り直接羽根の取付角度を変化させている斜流水車に適用
する場合には、出力軸１１に変則比の大なる減速機を取
付け、この減速機の出力軸の回転により直接羽根の取付
角度を変化させるのが好ましい。In the above first and second embodiments,
In both of them, the rotation difference between the output shaft 11 and the rotary main shaft 1 is once converted into a linear motion and the blade mounting angle is changed by this linear motion, but the present invention is not limited to such an example. The blade mounting angle may be directly changed by rotating the output shaft. For example, when the present invention is applied to a mixed flow turbine in which the blade mounting angle is directly changed by the rotation of the normal operation shaft, a speed reducer having a large irregular ratio is attached to the output shaft 11, and the output of the speed reducer is increased. It is preferable to directly change the mounting angle of the blade by rotating the shaft.
【００３５】[0035]
【発明の効果】本発明は、上述のように羽根の取付角度
変更のために油圧シリンダを使用しないので、高圧用の
シール機構が不用であり、シール機構の焼付、油漏れ等
の事故を防止することができ、同調速度は遊星歯車と変
速機の歯数で決まるので、正確で経年変化も受けない等
のメリットがある。さらに電動機の駆動量と羽根の角度
変化量が比例するので、羽根角度検出の簡素化が図れ、
回転主軸の回転運動を同調速度に変換して電動機の運動
に加算しているので電動機の動力に無駄がなく、また入
力軸を太陽歯車に接続しているので駆動トルクが低く故
障時の対応が容易となる。さらに歯車機構部は潤滑油を
充填したケース内に収納することによって十分潤滑さ
せ、作動の信頼性を向上させることができる。As described above, according to the present invention, since the hydraulic cylinder is not used for changing the mounting angle of the blade as described above, the seal mechanism for high pressure is unnecessary, and the accident such as seizure of the seal mechanism and oil leakage is prevented. Since the tuning speed is determined by the number of teeth of the planetary gear and the transmission, it has the merit of being accurate and not subject to secular change. Furthermore, since the drive amount of the electric motor is proportional to the change amount of the blade angle, the blade angle detection can be simplified.
Since the rotary motion of the rotary spindle is converted into the synchronized speed and added to the motion of the motor, there is no waste in the power of the motor, and because the input shaft is connected to the sun gear, the drive torque is low and it is possible to cope with failures. It will be easy. Further, the gear mechanism portion can be sufficiently lubricated by being housed in a case filled with lubricating oil to improve the reliability of operation.
【図１】本発明の第１の実施例の要部断面図。FIG. 1 is a sectional view of a main part of a first embodiment of the present invention.
【図２】本発明の可変ピッチプロペラ駆動装置の概略構
成を示す全体図。FIG. 2 is an overall view showing a schematic configuration of a variable pitch propeller drive device of the present invention.
【図３】本発明装置の作動説明図。FIG. 3 is an operation explanatory view of the device of the present invention.
【図４】本発明装置の作動説明図。FIG. 4 is an operation explanatory view of the device of the present invention.
【図５】本発明の他の実施例を示す要部断面図。FIG. 5 is a cross-sectional view of main parts showing another embodiment of the present invention.
１ 回転主軸 １ａ ランナボス ３ 羽根 ４ 操作ロッド ７ 入力軸 １０ 電動機 １１ 出力軸 １１ａ ねじ部 １５ ケース １６ 固定軸 ２１、２６ 太陽歯車 ２２、２７ 遊星歯車 ２４ 内歯歯車 ３１ 傘歯車 ３２ 遊星傘歯車 ３５、３６、３７、３８ 平歯車 DESCRIPTION OF SYMBOLS 1 rotary main shaft 1a runner boss 3 blade 4 operation rod 7 input shaft 10 electric motor 11 output shaft 11a screw part 15 case 16 fixed shaft 21, 26 sun gear 22, 27 planetary gear 24 internal gear 31 bevel gear 32 planetary bevel gear 35, 36 , 37, 38 Spur gears
Claims (2)
対的に回転させることにより、回転主軸に取付けられた
可変ピッチ羽根の取付角度を変化させる可変ピッチプロ
ペラ駆動装置において、入力軸を介して電動機に連結さ
れた太陽歯車と、この太陽歯車と噛合し自転しながら上
記太陽歯車の外周を公転する遊星歯車と、この遊星歯車
と噛合する第３の歯車からなる歯車列を有し、上記遊星
歯車又は第３の歯車のいずれか一方の歯車を前記出力軸
に連結するとともに、他方の歯車を固定軸と前記回転主
軸との間に介装された変速装置によって駆動し、前記太
陽歯車が停止しているとき、前記出力軸と回転主軸との
回転速度が等しくなるように変速比を選定したことを特
徴とする、可変ピッチプロペラ駆動装置。1. A variable pitch propeller drive device for changing the mounting angle of a variable pitch vane mounted on a rotating main shaft by relatively rotating an output shaft arranged concentrically with the rotating main shaft. A gear train composed of a sun gear connected to an electric motor via a planetary gear, a planetary gear that revolves around the outer periphery of the sun gear while meshing with the sun gear, and a third gear meshing with the planetary gear. , One of the planetary gear and the third gear is connected to the output shaft, and the other gear is driven by a transmission device interposed between a fixed shaft and the rotating main shaft, A variable pitch propeller drive device characterized in that the gear ratio is selected so that the rotation speeds of the output shaft and the rotary main shaft become equal to each other when the gear is stopped.
したケース内に収納するとともに、そのケースを回転主
軸に一体的に連結したことを特徴とする、請求項１記載
の可変ピッチプロペラ駆動装置。2. The variable pitch propeller drive according to claim 1, wherein the planetary gear mechanism and the transmission are housed in a case filled with lubricating oil, and the case is integrally connected to a main shaft of rotation. apparatus.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25133991A JP3363163B2 (en) | 1991-09-30 | 1991-09-30 | Variable pitch propeller drive |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP25133991A JP3363163B2 (en) | 1991-09-30 | 1991-09-30 | Variable pitch propeller drive |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH0587037A true JPH0587037A (en) | 1993-04-06 |
| JP3363163B2 JP3363163B2 (en) | 2003-01-08 |
Family
ID=17221356
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP25133991A Expired - Lifetime JP3363163B2 (en) | 1991-09-30 | 1991-09-30 | Variable pitch propeller drive |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3363163B2 (en) |
Cited By (8)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20110063670A (en) * | 2008-09-17 | 2011-06-13 | 베리 프로펄션 테크놀로지 에이비 | Propeller |
| CN102943737A (en) * | 2012-12-04 | 2013-02-27 | 浙江大学 | Ocean current energy generating set |
| CN103161886A (en) * | 2013-01-17 | 2013-06-19 | 杨克伟 | Double-power combined-current coaxial output speed adjusting device |
| CN110294093A (en) * | 2019-07-12 | 2019-10-01 | 胡泽兵 | A kind of ship propulsion device that paddle is adjusted by rotation |
| WO2021187541A1 (en) | 2020-03-17 | 2021-09-23 | 日本精工株式会社 | Thrust generating device |
| JP2021146823A (en) * | 2020-03-17 | 2021-09-27 | 日本精工株式会社 | Thrust generator |
| JP2021146826A (en) * | 2020-03-17 | 2021-09-27 | 日本精工株式会社 | Thrust generator |
| JP2021146821A (en) * | 2020-03-17 | 2021-09-27 | 日本精工株式会社 | Thrust generator |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JP6004876B2 (en) * | 2012-10-03 | 2016-10-12 | 三菱重工業株式会社 | Steering machine and ship equipped with the same |
| JP5826164B2 (en) * | 2012-12-28 | 2015-12-02 | 三菱重工業株式会社 | Steering machine |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60153479A (en) * | 1984-01-23 | 1985-08-12 | Ebara Corp | Device for opening and closing runner vane |
-
1991
- 1991-09-30 JP JP25133991A patent/JP3363163B2/en not_active Expired - Lifetime
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS60153479A (en) * | 1984-01-23 | 1985-08-12 | Ebara Corp | Device for opening and closing runner vane |
Cited By (10)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| KR20110063670A (en) * | 2008-09-17 | 2011-06-13 | 베리 프로펄션 테크놀로지 에이비 | Propeller |
| CN102943737A (en) * | 2012-12-04 | 2013-02-27 | 浙江大学 | Ocean current energy generating set |
| CN103161886A (en) * | 2013-01-17 | 2013-06-19 | 杨克伟 | Double-power combined-current coaxial output speed adjusting device |
| CN110294093A (en) * | 2019-07-12 | 2019-10-01 | 胡泽兵 | A kind of ship propulsion device that paddle is adjusted by rotation |
| WO2021187541A1 (en) | 2020-03-17 | 2021-09-23 | 日本精工株式会社 | Thrust generating device |
| JP2021146823A (en) * | 2020-03-17 | 2021-09-27 | 日本精工株式会社 | Thrust generator |
| JP2021146826A (en) * | 2020-03-17 | 2021-09-27 | 日本精工株式会社 | Thrust generator |
| JP2021146821A (en) * | 2020-03-17 | 2021-09-27 | 日本精工株式会社 | Thrust generator |
| JP6969711B1 (en) * | 2020-03-17 | 2021-11-24 | 日本精工株式会社 | Thrust generator |
| US11718387B2 (en) | 2020-03-17 | 2023-08-08 | Nsk Ltd. | Propellant force generator |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3363163B2 (en) | 2003-01-08 |
Similar Documents
| Publication | Publication Date | Title |
|---|---|---|
| JP5173454B2 (en) | Turboprop with variable pitch propeller | |
| US6926636B2 (en) | Gear driven power converter | |
| JP2742113B2 (en) | Prop fan / turbo prop engine with rotor blade adjustment device | |
| US6527662B2 (en) | Pump drive apparatus | |
| JPH06520B2 (en) | Counter-rotating propeller drive for marine | |
| JPH0587037A (en) | Variable pitch propeller driving device | |
| US6119542A (en) | Compact toothed wheel gearing with large gear ratio | |
| US5352162A (en) | Dual concentric positively infinitely variable rotary motion transmission | |
| JP2576839B2 (en) | Stroke adjusting device for reciprocating pump | |
| JPH10246173A (en) | Planetary accelerator | |
| US4521158A (en) | Fluid-flow machine | |
| EP0233303B1 (en) | Planetary gear apparatus | |
| US4454779A (en) | Drive for a variable-stroke swash plate mechanism | |
| JPH07507623A (en) | Planetary transmission with two driven shafts | |
| CN214036723U (en) | Stepless speed change mechanism | |
| JP2023529245A (en) | fan wheel | |
| JP2001099045A (en) | Blade pitch variable mechanism for wind mill | |
| US4878809A (en) | Power source and control mechanism for propeller pitch control | |
| CN2673500Y (en) | Planetary type ball mill | |
| US5807199A (en) | Hydro-mechanical gearbox | |
| JP3919849B2 (en) | Variable pitch propeller drive unit | |
| EP0216540A1 (en) | Rotary power transmission apparatus | |
| JPH0874723A (en) | Variable pitch propeller driving device | |
| JP3599760B2 (en) | Variable pitch propeller drive | |
| JPS6347658Y2 (en) |
Legal Events
| Date | Code | Title | Description |
|---|---|---|---|
| S111 | Request for change of ownership or part of ownership |
Free format text: JAPANESE INTERMEDIATE CODE: R313115 |
|
| R360 | Written notification for declining of transfer of rights |
Free format text: JAPANESE INTERMEDIATE CODE: R360 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| R250 | Receipt of annual fees |
Free format text: JAPANESE INTERMEDIATE CODE: R250 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20081025 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20081025 Year of fee payment: 6 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20091025 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20091025 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20091025 Year of fee payment: 7 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20101025 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20101025 Year of fee payment: 8 |
|
| S531 | Written request for registration of change of domicile |
Free format text: JAPANESE INTERMEDIATE CODE: R313531 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20101025 Year of fee payment: 8 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| S531 | Written request for registration of change of domicile |
Free format text: JAPANESE INTERMEDIATE CODE: R313531 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20101025 Year of fee payment: 8 |
|
| R350 | Written notification of registration of transfer |
Free format text: JAPANESE INTERMEDIATE CODE: R350 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20101025 Year of fee payment: 8 |
|
| FPAY | Renewal fee payment (event date is renewal date of database) |
Free format text: PAYMENT UNTIL: 20111025 Year of fee payment: 9 |
|
| EXPY | Cancellation because of completion of term |