JP2005233277A - Gear meshing structure of planetary gear device - Google Patents

Gear meshing structure of planetary gear device Download PDF

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Publication number
JP2005233277A
JP2005233277A JP2004041674A JP2004041674A JP2005233277A JP 2005233277 A JP2005233277 A JP 2005233277A JP 2004041674 A JP2004041674 A JP 2004041674A JP 2004041674 A JP2004041674 A JP 2004041674A JP 2005233277 A JP2005233277 A JP 2005233277A
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Prior art keywords
gear
sun gear
carrier
shaft
sun
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Hitoshi Miyamoto
仁 宮本
Tomoyuki Takahashi
知之 高橋
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Komatsu Ltd
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Komatsu Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H37/00—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00
    • F16H37/02—Combinations of mechanical gearings, not provided for in groups F16H1/00 - F16H35/00 comprising essentially only toothed or friction gearings
    • F16H37/04—Combinations of toothed gearings only
    • F16H37/041—Combinations of toothed gearings only for conveying rotary motion with constant gear ratio
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/28—Toothed gearings for conveying rotary motion with gears having orbital motion
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16H—GEARING
    • F16H1/00—Toothed gearings for conveying rotary motion
    • F16H1/02—Toothed gearings for conveying rotary motion without gears having orbital motion
    • F16H1/20—Toothed gearings for conveying rotary motion without gears having orbital motion involving more than two intermeshing members
    • Y—GENERAL TAGGING OF NEW TECHNOLOGICAL DEVELOPMENTS; GENERAL TAGGING OF CROSS-SECTIONAL TECHNOLOGIES SPANNING OVER SEVERAL SECTIONS OF THE IPC; TECHNICAL SUBJECTS COVERED BY FORMER USPC CROSS-REFERENCE ART COLLECTIONS [XRACs] AND DIGESTS
    • Y02—TECHNOLOGIES OR APPLICATIONS FOR MITIGATION OR ADAPTATION AGAINST CLIMATE CHANGE
    • Y02E—REDUCTION OF GREENHOUSE GAS [GHG] EMISSIONS, RELATED TO ENERGY GENERATION, TRANSMISSION OR DISTRIBUTION
    • Y02E10/00—Energy generation through renewable energy sources
    • Y02E10/70—Wind energy
    • Y02E10/72—Wind turbines with rotation axis in wind direction

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Wind Motors (AREA)
  • Retarders (AREA)
  • General Details Of Gearings (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a gear meshing structure of a planetary gear device capable of enhancing the durability of a sun gear and a carrier by preventing the sun gear from contacting with the carrier. <P>SOLUTION: The gear meshing structure of the planetary gear device includes a restraining means to restrain the axial direction movement of the sun gear 6. The restraining means is equipped with a ring-shaped groove 6c installed at the periphery of a cylindrical body part 6a beside the teeth part 6b of the sun gear 6 about the axial direction, half split spacers 41 formed by dividing a ring plate approximately in two halves to be inserted into the groove 6c, the ring plate having an outside diameter greater than the outside diameter of the periphery of the body part 6a, and a plate 42 to fix the spacer halves 41 inserted into the groove 6c in such a way as pinching together with the end face of a gear supporting shaft 23 coupled with the sun gear 6 rigidly. The restraining means may be a bearing 43 installed between the cylindrical body part 6a of the sun gear 6 and the carrier 9 or a pipe 5 fixed thereto. <P>COPYRIGHT: (C)2005,JPO&NCIPI

Description

本発明は、遊星歯車装置の歯車締結構造に関する。   The present invention relates to a gear fastening structure of a planetary gear device.

従来から、減速比が大きく、しかもコンパクトに構成できるという理由によって、遊星歯車装置が多く用いられている。例えば、風力発電機の回転翼と発電機との間に設置される遊星歯車装置としては、特許文献１（未公開）に開示された風力発電用増速機がある。図４は特許文献１に記載された風力発電用増速機の断面図であり、以下図４に基づき従来技術を説明する。 Conventionally, planetary gear devices are often used because they have a large reduction ratio and can be made compact. For example, as a planetary gear device installed between a rotor blade of a wind power generator and a power generator, there is a wind power booster disclosed in Patent Document 1 (unpublished). FIG. 4 is a cross-sectional view of a wind power booster described in Patent Document 1, and the prior art will be described based on FIG.

図４において、風力発電用増速機は、入力側歯車機構（低速側歯車機構）１と出力側歯車機構（高速側歯車機構）２とを備え、回転翼（図示せず）の軸部が入力側歯車機構１に接続され、この回転翼が風を受けて回転してその回転力が出力軸４に伝達されるものである。
入力側歯車機構１は、太陽歯車６と、この太陽歯車６に噛合する複数（この場合、３個の例を示している。）の遊星歯車７…と、この遊星歯車７が噛合するリングギヤ８と、遊星歯車７…を回転自在に支持するキャリア９等を備えている。太陽歯車６の中心には貫通孔が形成されており、該貫通孔にはキャリア９に取り付けられたパイプ５が回転自在に挿入されている。太陽歯車６は、筒状本体部６ａと、この筒状本体部６ａの外周面に設けられる歯部６ｂとから構成されている。 In FIG. 4, the wind power speed increaser includes an input side gear mechanism (low speed side gear mechanism) 1 and an output side gear mechanism (high speed side gear mechanism) 2, and a shaft portion of a rotor blade (not shown) is provided. Connected to the input side gear mechanism 1, the rotating blades receive wind and rotate to transmit the rotational force to the output shaft 4.
The input side gear mechanism 1 includes a sun gear 6, a plurality of (in this case, three examples) planetary gears 7 meshed with the sun gear 6, and a ring gear 8 meshed with the planetary gear 7. And a carrier 9 for rotatably supporting the planetary gears 7. A through hole is formed at the center of the sun gear 6, and a pipe 5 attached to the carrier 9 is rotatably inserted into the through hole. The sun gear 6 includes a cylindrical main body portion 6a and tooth portions 6b provided on the outer peripheral surface of the cylindrical main body portion 6a.

キャリア９は、１対の円盤状の基板部１１，１２を有しており、この１対の基板部１１，１２が周方向に沿って所定ピッチ（この場合、約１２０度ピッチ）で配設される連結部１４…にて連結されている。そして、周方向に沿って隣合う連結部１４、１４間には、基板部１１、１２間にそれぞれ軸部材１５を固定し、この軸部材１５に軸受１６、１６を介して回転自在に前記遊星歯車７を外嵌している。キャリア９は、ケース１０のギヤケース１８に軸受２１を介して、トルクアーム１７に軸受２０を介して回転自在に支持されている。また、前記パイプ５は、その一端部がキャリア９の基板部１１に固着され、他端部が出力側歯車機構２の歯車支持軸２３に軸受を介して回転自在に支持されている。一方の基板部１１から外方へ突出して設けた円筒部１３に、前記回転翼の軸部が連結される。また、ケース１０のギヤケース１８とトルクアーム１７との間には前記リングギヤ８が設けられている。 The carrier 9 has a pair of disk-shaped substrate portions 11 and 12, and the pair of substrate portions 11 and 12 are arranged at a predetermined pitch (in this case, a pitch of about 120 degrees) along the circumferential direction. Are connected by connecting portions 14. And between the connection parts 14 and 14 adjacent along the circumferential direction, the shaft member 15 is fixed between the board | substrate parts 11 and 12, respectively, The said planetary body is freely rotatable to this shaft member 15 via the bearings 16 and 16. A gear 7 is externally fitted. The carrier 9 is rotatably supported by the gear case 18 of the case 10 via a bearing 21 and the torque arm 17 via a bearing 20 . Further, one end of the pipe 5 is fixed to the substrate portion 11 of the carrier 9 , and the other end is rotatably supported on the gear support shaft 23 of the output side gear mechanism 2 via a bearing. The shaft portion of the rotor blade is connected to a cylindrical portion 13 that protrudes outward from one substrate portion 11. The ring gear 8 is provided between the gear case 18 of the case 10 and the torque arm 17 .

出力側歯車機構（高速側歯車機構）２は、前記歯車支持軸２３に外嵌される第１歯車２５と、この第１歯車２５に噛合する歯部が設けられた軸部材（図示せず）の回転によって回転する第２歯車（図示せず）と、この第２歯車に噛合してこの第２歯車の回転によって回転する前記出力軸４とを有している。歯車支持軸２３は、前記太陽歯車６の筒状本体部６ａに連続する筒状体であって、筒状本体部６ａと軸継手２３ａを介してスプライン又は歯車継手結合されており、一体に回転する。歯車支持軸２３は、軸受３１、３２を介して回転自在に回転し、歯車支持軸２３及び前記第１歯車２５に設けられた軸継手部３７（スプライン又は歯車継手）を介して前記第１歯車２５が回転する。 The output side gear mechanism (high speed side gear mechanism) 2 is a shaft member (not shown) provided with a first gear 25 fitted on the gear support shaft 23 and a tooth portion meshing with the first gear 25. A second gear (not shown) that rotates by rotation of the second gear, and the output shaft 4 that meshes with the second gear and rotates by rotation of the second gear. The gear support shaft 23 is a cylindrical body that is continuous with the cylindrical main body portion 6a of the sun gear 6, and is coupled to the cylindrical main body portion 6a and the shaft joint 23a through a spline or gear joint, and rotates integrally. To do. The gear support shaft 23 rotates rotatably through bearings 31 and 32, and the first gear is connected to the gear support shaft 23 and a shaft joint portion 37 (spline or gear joint) provided on the first gear 25. 25 rotates.

また、前記第２歯車は、ギヤケース１８に軸受（図示せず）を介して回転自在に支持された軸部材（図示せず）の一端部に外嵌固定されている。この軸部材の他端部には、第１歯車２５に噛合する歯部（図示せず）が設けられている。出力軸４の一端部には、前記第２歯車に噛合するピニオン（ギヤ部）３０が設けられている。 The second gear is externally fixed to one end portion of a shaft member (not shown) rotatably supported by a gear case 18 via a bearing (not shown). A tooth portion (not shown) that meshes with the first gear 25 is provided at the other end portion of the shaft member . One end of the output shaft 4 is provided with a pinion (gear portion) 30 that meshes with the second gear.

特許願２００３−４０４５８４号公報（平成１５年１２月３日出願）Japanese Patent Application No. 2003-404584 (filed on December 3, 2003)

しかしながら、上記従来の遊星歯車装置においては、次のような問題が生じている。すなわち、入力側歯車機構１の太陽歯車６は、歯部６ｂで複数の遊星歯車７に噛合しており、各遊星歯車７の荷重分担を向上させる目的のため、軸継手２３ａでフロートさせる、つまり軸継手２３ａを介することにより半径方向に移動自在となるように外嵌されている。ところが、太陽歯車６の筒状本体部６ａは、出力側歯車機構２の歯車支持軸２３と軸継手２３ａによってスプライン等を介して一体的に回転可能となっており、軸方向にも移動可能な構成となっている。このため、太陽歯車６が回転中にキャリア９のスラスト面９ａと接触することがある。太陽歯車６とキャリア９のスラスト面９ａとの間には相対回転が生じているので、上記接触による太陽歯車６及びキャリア９のスラスト面９ａの摺動部の磨耗が激しく、部品寿命を劣化させている。特に、風力発電機では、発電制御用の油圧配管や電気配線を軸方向に貫通させるために、本来遊星歯車装置の動力伝達には不要であるパイプ５を太陽歯車６の中心部に設けている。このため、太陽歯車６の前記摺動部の径が大きくなり、太陽歯車６及びキャリア９の摺動部の周速度は従来よりも速くなり、摺動部の磨耗度が激しい。さらに、風力発電機等は高い塔の上部に設置されているため、部品故障時のメンテナンスは非常に困難である。この結果、部品の耐久性を大幅に向上することが強く望まれている。 However, the conventional planetary gear device has the following problems. That is, the sun gear 6 of the input side gear mechanism 1 meshes with the plurality of planetary gears 7 at the tooth portions 6b, and is floated at the shaft coupling 23a for the purpose of improving the load sharing of each planetary gear 7. It is externally fitted so as to be movable in the radial direction through the shaft coupling 23a . However, the cylindrical body portion 6a of the sun gear 6, an output-side gear mechanism has a rotatable integrally via the splines by the second gear support shaft 23 and shaft coupling 23a, which can also be moved in the axial direction It has a configuration. For this reason, the sun gear 6 may come into contact with the thrust surface 9a of the carrier 9 during rotation. Since the relative rotation is generated between the thrust face 9a of the sun gear 6 and the carrier 9, the wear of the sliding portion of the thrust face 9a of the sun gear 6 and the carrier 9 by the contact is intense, degrade part life ing. In particular, in a wind power generator , a pipe 5 that is essentially unnecessary for power transmission of the planetary gear device is provided at the center of the sun gear 6 in order to penetrate the hydraulic piping and electric wiring for power generation control in the axial direction . . For this reason, the diameter of the said sliding part of the sun gear 6 becomes large, the peripheral speed of the sliding part of the sun gear 6 and the carrier 9 becomes faster than before, and the degree of wear of the sliding part is intense. Furthermore, since wind power generators and the like are installed at the upper part of a high tower, maintenance at the time of component failure is very difficult. As a result, it is strongly desired to greatly improve the durability of the parts.

本発明は、上記の問題点に着目してなされたもので、太陽歯車とキャリアとの接触を防止して、太陽歯車及びキャリアの耐久性を向上できる遊星歯車装置の歯車締結構造を提供することを目的としている。   The present invention has been made paying attention to the above-mentioned problems, and provides a gear fastening structure for a planetary gear device that can prevent the contact between the sun gear and the carrier and improve the durability of the sun gear and the carrier. It is an object.

上記目的を達成するために、第１発明は、遊星歯車装置の歯車締結構造において、太陽歯車の軸方向移動を拘束する拘束手段を設けたことを特徴としている。   In order to achieve the above object, the first invention is characterized in that in the gear fastening structure of the planetary gear device, a restraining means for restraining the axial movement of the sun gear is provided.

この場合において、前記拘束手段は、
前記太陽歯車の歯部の軸方向側方で筒状本体部の外周部に設けた環状溝と、
前記太陽歯車の筒状本体部の外周部の外径よりも大きな外径を有する環状プレートを略半分割にして構成され、前記環状溝内に環状に配置して挿入される２つの半割スペーサと、
前記環状溝内に挿入した前記２つの半割スペーサを、前記太陽歯車に一体的に回転自在に結合された歯車支持軸の端面とで挟むようにして固定するプレートとを備えてもよい。 In this case, the restraining means is
An annular groove provided on the outer periphery of the cylindrical main body at the axial side of the tooth portion of the sun gear;
Two half spacers, which are formed by dividing an annular plate having an outer diameter larger than the outer diameter of the outer peripheral portion of the cylindrical main body portion of the sun gear into a substantially half-divided shape, and are arranged annularly in the annular groove. When,
A plate for fixing the two halved spacers inserted into the annular groove so as to be sandwiched between end faces of a gear support shaft that is integrally and rotatably coupled to the sun gear .

また、この場合において、前記拘束手段は、前記太陽歯車の筒状本体部と、キャリア又はキャリアに固定されたパイプとの間に設けた軸受であってもよい。 In this case, the restraining means may be a bearing provided between the cylindrical main body of the sun gear and a carrier or a pipe fixed to the carrier .

第１発明によると、太陽歯車の軸方向移動を拘束しているので、太陽歯車とキャリアとの所定の隙間を維持できる。これにより、太陽歯車とキャリアとの接触による磨耗を無くし、太陽歯車及びキャリアの耐久性、すなわち遊星歯車装置の耐久性を大幅に向上できる。   According to the first invention, since the movement of the sun gear in the axial direction is restricted, a predetermined gap between the sun gear and the carrier can be maintained. This eliminates wear due to contact between the sun gear and the carrier, and can greatly improve the durability of the sun gear and the carrier, that is, the durability of the planetary gear device.

また、第２発明によると、太陽歯車は、太陽歯車に一体的に回転自在に結合された歯車支持軸に半割スペーサを介して固定されているため、軸方向移動が拘束され、太陽歯車とキャリアとの所定の隙間を維持できる。このため、太陽歯車とキャリアとの接触による磨耗を防止でき、遊星歯車装置の耐久性を向上できる。 According to the second invention, since the sun gear is fixed to the gear support shaft that is integrally and rotatably coupled to the sun gear via the half spacer, the axial movement is restricted, and the sun gear A predetermined gap with the carrier can be maintained. For this reason, wear due to contact between the sun gear and the carrier can be prevented, and the durability of the planetary gear device can be improved.

また、第３発明によると、太陽歯車をキャリア又はキャリアに固定されたパイプの外周部に軸受を介して外嵌しているので、この軸受により太陽歯車のキャリアに向かう方向への移動が拘束される。このため、太陽歯車とキャリアとの所定隙間を維持できるので、両者同士の接触による磨耗を防止して、遊星歯車装置の耐久性を向上できる。 According to the third invention, since the sun gear is externally fitted to the carrier or the outer peripheral portion of the pipe fixed to the carrier via the bearing, the movement of the sun gear toward the carrier is restricted by the bearing. The For this reason, since the predetermined clearance gap between a sun gear and a carrier can be maintained, the abrasion by contact of both can be prevented and the durability of a planetary gear apparatus can be improved.

以下、本発明に係る遊星歯車装置の歯車締結構造の好適な実施形態について、図面を参照して説明する。尚、適合機械として風力発電機を例に挙げて説明する。   DESCRIPTION OF EXEMPLARY EMBODIMENTS Hereinafter, a preferred embodiment of a gear fastening structure of a planetary gear device according to the invention will be described with reference to the drawings. Note that a wind power generator will be described as an example of a suitable machine.

まず、図１に基づき、第１実施形態を説明する。
図１において、風力発電用増速機は、入力側歯車機構（低速側歯車機構）１と出力側歯車機構（高速側歯車機構）２とを備えており、入力側歯車機構１に回転翼（図示せず）の軸部が接続され、この回転翼が風を受けて回転してその回転力が出力側歯車機構２の出力軸４に伝達されるものである。 First, a first embodiment will be described with reference to FIG.
In FIG. 1, the wind power speed increaser includes an input side gear mechanism (low speed side gear mechanism) 1 and an output side gear mechanism (high speed side gear mechanism) 2. A shaft portion (not shown) is connected, the rotor blades receive wind and rotate, and the rotational force is transmitted to the output shaft 4 of the output side gear mechanism 2.

入力側歯車機構１は、前記回転翼に直結する軸部に固定されたキャリア９と、このキャリア９に回転自在に支持された複数（例えば３個）の遊星歯車７（１個のみ図示している。）と、この遊星歯車７と噛合する太陽歯車６とリングギヤ８とを備えている。パイプ５は、詳細は後述するようにキャリア９に取り付けられ、パイプ５の一端側には上記太陽歯車６が回転自在に挿入されている。パイプ５はパイプ状部材から構成されており、パイプ５の貫通孔内に風力発電の各種制御を行うための油圧配管や電気配線（いずれも図示せず）を通すようにしている。太陽歯車６は、パイプ５に回転自在に挿入される筒状本体部６ａと、この筒状本体部６ａの外周面の一端側に設けられる歯部６ｂとから構成されている。 The input side gear mechanism 1 includes a carrier 9 fixed to a shaft portion directly connected to the rotor blade, and a plurality of (for example, three) planetary gears 7 (for example, only one is illustrated) supported rotatably on the carrier 9. And a sun gear 6 and a ring gear 8 that mesh with the planetary gear 7 . The pipe 5 is attached to a carrier 9 as will be described in detail later, and the sun gear 6 is rotatably inserted into one end side of the pipe 5. The pipe 5 is composed of a pipe-like member, and hydraulic piping and electrical wiring (none of which are not shown) for performing various controls of wind power generation are passed through the through holes of the pipe 5. The sun gear 6 includes a cylindrical main body portion 6a that is rotatably inserted into the pipe 5 and a tooth portion 6b provided on one end side of the outer peripheral surface of the cylindrical main body portion 6a.

キャリア９は、１対の円盤状の基板部１１，１２を有しており、１対の基板部１１，１２が周方向に沿って所定ピッチ（遊星歯車７が３個の場合、約１２０度ピッチ）で配設される複数箇所の連結部１４…にて連結されている。周方向に沿って隣合う連結部１４、１４間には、前記基板部１１、１２間にそれぞれ軸部材１５を固定し、軸部材１５に軸受１６、１６を介して回転自在に前記遊星歯車７を外嵌している。前記ケース１０は、トルクアーム１７と、リングギヤ８と、出力軸４側のギヤケース１８とを有しており、キャリア９はこのケース１０のトルクアーム１７に軸受２０を介して、ギヤケース１８に軸受２１を介してそれぞれ回転自在に支持されている。また、前記パイプ５は、その一端部がキャリア９の入力軸側の基板部１１に取り付けられており、他端部が出力側歯車機構２の歯車支持軸２３に軸受３８を介して回転自在に支持されている。キャリア９の入力軸側の基板部１１には外方へ突出する円筒部１３が設けられており、この円筒部１３には回転翼（図示せず）の軸部が連結される。円筒部１３と、キャリア９の基板１１の一部と、パイプ５とは一体的に回転するようになっており、以下、これら円筒部１３と、キャリア９の基板１１の一部と、パイプ５とをもって入力軸１９と呼ぶ。 The carrier 9 has a pair of disk-shaped substrate portions 11 and 12, and the pair of substrate portions 11 and 12 has a predetermined pitch along the circumferential direction (when there are three planetary gears 7, about 120 degrees). Are connected by a plurality of connecting portions 14 arranged at a pitch). A shaft member 15 is fixed between the substrate portions 11 and 12 between the connecting portions 14 and 14 adjacent to each other in the circumferential direction, and the planetary gear 7 is rotatable on the shaft member 15 via bearings 16 and 16. Is fitted. The case 10 has a torque arm 17, a ring gear 8, and a gear case 18 on the output shaft 4 side. The carrier 9 is connected to the torque arm 17 of the case 10 via a bearing 20, and to the gear case 18 to a bearing 21. Each is supported rotatably via each other. The pipe 5 has one end attached to the substrate 11 on the input shaft side of the carrier 9 and the other end rotatable to the gear support shaft 23 of the output side gear mechanism 2 via a bearing 38. It is supported. A cylindrical portion 13 protruding outward is provided on the substrate portion 11 on the input shaft side of the carrier 9, and a shaft portion of a rotary blade (not shown) is connected to the cylindrical portion 13. The cylindrical portion 13, a part of the substrate 11 of the carrier 9, and the pipe 5 rotate integrally. Hereinafter, the cylindrical portion 13, a part of the substrate 11 of the carrier 9, and the pipe 5 are rotated. Is called the input shaft 19.

ケース１０のトルクアーム１７とギヤケース１８との間には、前記リングギヤ８が取り付けられている。なお、トルクアーム１７の、入力軸１９の円筒部１３の外周側、及びパイプ５の他端部の外周側には、それぞれシール部Ｓ、Ｓが配置されている。なおまた、ケース１０はトルクアーム１７とギヤケース１８とリングギヤ８とで分割構成された例で示しているが、これに限定されず、例えば一体的に構成してもよい。 The ring gear 8 is attached between the torque arm 17 and the gear case 18 of the case 10. Seal portions S and S are arranged on the outer peripheral side of the cylindrical portion 13 of the input shaft 19 and the outer peripheral side of the other end portion of the pipe 5 of the torque arm 17, respectively. In addition, the case 10 is shown as an example in which the torque arm 17, the gear case 18, and the ring gear 8 are divided and configured, but the present invention is not limited to this, and may be configured integrally, for example.

上記のように構成された入力側歯車機構１では、前記回転翼が風を受けて回転すれば、入力軸１９が図１の矢印Ａ１方向に回転し、この入力軸１９の回転に伴ってキャリア９が回転して、遊星歯車７がリングギヤ８に噛合しながら太陽歯車６の廻りに公転しつつ自転する。これによって、太陽歯車６が歯車支持軸２３の軸心の回りに回転する。 In the input side gear mechanism 1 configured as described above, when the rotor blades receive wind and rotate, the input shaft 19 rotates in the direction of the arrow A1 in FIG. 9 rotates and the planetary gear 7 rotates while revolving around the sun gear 6 while meshing with the ring gear 8. As a result, the sun gear 6 rotates around the axis of the gear support shaft 23 .

次に、出力側歯車機構２は、歯車支持軸２３を介して外嵌される第１歯車２５と、この第１歯車２５に噛合う歯部２９を有する軸部材２８の回転によって回転する第２歯車２６と、この第２歯車２６に噛合してこの第２歯車２６の回転によって回転する前記出力軸４とを有している。歯車支持軸２３は、前記太陽歯車６の筒状本体部６ａに連結した筒状体であって、太陽歯車６の筒状本体部６ａと一体に回転する。すなわち、一方の歯車支持軸２３の一端部には、前記筒状本体部６ａの歯車支持軸２３側外径よりも大きな内径を有する拡径部２３ｂを形成しており、拡径部２３ｂの内周部にはスプライン２４ａ等の軸継手を形成している。他方の太陽歯車６の筒状本体部６ａの歯車支持軸２３側の外周部にはスプライン２４ｂ等の軸継手を形成してあり、このスプライン２４ｂよりも歯部６ｂ側（入力側）の外周部には環状溝６ｃを形成している。そして、この環状溝６ｃ内に、２つの半割スペーサ４１，４１を環状にして挿入している。この２つの半割スペーサ４１，４１は、前記筒状本体部６ａのスプライン２４ｂの外周部外径よりも大きな外径を有する環状プレートを略半分に分割して形成したものである。環状溝６ｃと半割スペーサ４１，４１との間の径方向隙間は、太陽歯車６が複数の遊星歯車７から偏荷重を受けたときに径方向に移動可能な程度の大きさに設定され、軸方向隙間は、太陽歯車６の軸方向の移動を拘束する程度に形成されている。さらに、筒状本体部６ａのスプライン２４ｂは前記歯車支持軸２３の拡径部２３ｂのスプライン２４ａに噛合うように挿入し、この歯車支持軸２３の拡径部２３ｂの端面を前記半割スペーサ４１，４１の端面に当接させ、この半割スペーサ４１，４１を挟むように歯車支持軸２３の外端面に環状プレート４２を当ててボルトで固定している。尚、太陽歯車６を径方向に移動可能とするために、ここでは２つの半割スペーサ４１，４１と太陽歯車６の環状溝６ｃとの間に所定の隙間を設けているが、これに限定されず、２つの半割スペーサ４１，４１と歯車支持軸２３の外端面及び環状プレート４２との隙間を、前記太陽歯車６が径方向に移動自在に設けてもよい。 Next, the output side gear mechanism 2 is rotated by rotation of the first gear 25 that is externally fitted through the gear support shaft 23 and the shaft member 28 that has the tooth portion 29 that meshes with the first gear 25. It has a gear 26 and the output shaft 4 that meshes with the second gear 26 and rotates by the rotation of the second gear 26. The gear support shaft 23 is a cylindrical body connected to the cylindrical main body portion 6 a of the sun gear 6, and rotates integrally with the cylindrical main body portion 6 a of the sun gear 6. That is, at one end portion of one gear support shaft 23, an enlarged diameter portion 23b having an inner diameter larger than the outer diameter of the cylindrical main body portion 6a on the gear support shaft 23 side is formed. A shaft coupling such as a spline 24a is formed on the peripheral portion. A shaft joint such as a spline 24b is formed on the outer peripheral portion of the cylindrical main body 6a of the other sun gear 6 on the gear support shaft 23 side, and the outer peripheral portion on the tooth portion 6b side (input side) of the spline 24b. Is formed with an annular groove 6c. The two half spacers 41 and 41 are inserted into the annular groove 6c in an annular shape. The two half spacers 41, 41 are formed by dividing an annular plate having an outer diameter larger than the outer diameter of the outer periphery of the spline 24b of the cylindrical main body 6a into approximately half. The radial gap between the annular groove 6c and the half spacers 41, 41 is set to a size that allows the sun gear 6 to move in the radial direction when the sun gear 6 receives an offset load from the plurality of planetary gears 7, The axial gap is formed to such an extent that the movement of the sun gear 6 in the axial direction is restricted. Further, the spline 24b of the cylindrical body 6a is inserted so as to mesh with the spline 24a of the enlarged diameter portion 23b of the gear support shaft 23, and the end face of the enlarged diameter portion 23b of the gear support shaft 23 is inserted into the half spacer 41. , 41, and an annular plate 42 is applied to the outer end surface of the gear support shaft 23 so as to sandwich the half spacers 41, 41 and fixed with bolts. In order to make the sun gear 6 movable in the radial direction, a predetermined gap is provided between the two half spacers 41 and 41 and the annular groove 6c of the sun gear 6 here. Alternatively, the sun gear 6 may be provided so that the gap between the two half spacers 41, 41 and the outer end surface of the gear support shaft 23 and the annular plate 42 is movable in the radial direction.

そして、ケース１０のギヤケース１８内に収納される前記第１歯車２５が、前記歯車支持軸２３の外周部に設けられたスプライン等の軸継手部３７により外嵌固定されている。歯車支持軸２３が回転すると、この軸継手部３７により前記第１歯車２５が回転する。 The first gear 25 housed in the gear case 18 of the case 10 is externally fixed by a shaft coupling portion 37 such as a spline provided on the outer peripheral portion of the gear support shaft 23. When the gear support shaft 23 is rotated, the first gear 25 is rotated by the shaft coupling portion 37 .

また、第２歯車２６は、ギヤケース１８に軸受２７、２７を介して回転自在に支持された軸部材２８の一端部に外嵌固定されている。軸部材２８は、出力軸４の近傍に配置されている。軸部材２８の他端部には、第１歯車２５に噛合する歯部２９が設けられている。また、前記出力軸４の一端部には、上記第２歯車２６に噛合するピニオン（ギヤ部）３０が設けられている。 The second gear 26 is externally fitted and fixed to one end of a shaft member 28 that is rotatably supported by the gear case 18 via bearings 27 and 27. The shaft member 28 is disposed in the vicinity of the output shaft 4. A tooth portion 29 that meshes with the first gear 25 is provided at the other end portion of the shaft member 28. A pinion (gear part) 30 that meshes with the second gear 26 is provided at one end of the output shaft 4.

上記出力側歯車機構２では、第１歯車２５が回転すれば、歯部２９が第１歯車２５と噛合している軸部材２８が回転する。さらに軸部材２８が回転すれば、第２歯車２６が回転して、この第２歯車２６にギヤ部３０が噛合している出力軸４が回転する。なお、出力軸４は、図１に示すように、その一端部が軸受３４を介してギヤケース１８のリングギヤ８側の側壁３５に回転自在に支持され、その他端部が軸受３６，３６を介してギヤケース１８の外端壁２２に回転自在に支持されている。また、前記各歯車機構１，２の各軸受１６，２０，２１，２７，３１，３２，３４，３６等は潤滑油が供給され、各回転体が滑らかに回転するように構成されている。 In the output side gear mechanism 2, when the first gear 25 rotates, the shaft member 28 in which the tooth portion 29 meshes with the first gear 25 rotates. When the shaft member 28 further rotates, the second gear 26 rotates, and the output shaft 4 in which the gear portion 30 is engaged with the second gear 26 rotates. As shown in FIG. 1, one end of the output shaft 4 is rotatably supported by a side wall 35 on the ring gear 8 side of the gear case 18 via a bearing 34, and the other end is supported by bearings 36, 36. The gear case 18 is rotatably supported by the outer end wall 22. The bearings 16, 20, 21, 27, 31, 32, 34, 36, etc. of the gear mechanisms 1, 2 are configured so that lubricating oil is supplied and the rotating bodies rotate smoothly.

従って、この増速機では、前述のように回転翼（図示せず）が風に当たることによって入力軸１９が図１の矢印Ａ１方向に回転すれば、キャリア９が回転して、遊星歯車７及びリングギヤ８を介して太陽歯車６が回転する。そして、太陽歯車６が回転すれば、この太陽歯車６の軸継手（スプライン２４ｂ）にて歯車支持軸２３が回転することになり、歯車支持軸２３の外周部に設けられた軸継手部３７が回転すれば、上記したように出力軸４が矢印Ａ２のように回転する。また、出力軸４は発電機（図示せず）等に接続されていて、この出力軸４の回転によって、発電機が駆動して発電されるようになっている。 Therefore, in this speed increaser, if the input shaft 19 rotates in the direction of the arrow A1 in FIG. 1 due to the rotor blades (not shown) hitting the wind as described above, the carrier 9 rotates, and the planetary gear 7 and The sun gear 6 rotates through the ring gear 8. And if the sun gear 6 rotates, the gear support shaft 23 will rotate in the shaft coupling (spline 24b) of this sun gear 6, and the shaft coupling part 37 provided in the outer peripheral part of the gear support shaft 23 will become. When rotating, the output shaft 4 rotates as shown by the arrow A2 as described above. The output shaft 4 is connected to a generator (not shown) or the like, and the generator is driven by the rotation of the output shaft 4 to generate power.

第１実施形態によると、太陽歯車６は半割スペーサ４１，４１を介して歯車支持軸２３に連結されており、この歯車支持軸２３は、軸受３１，３２を介してケース１０のギヤケース１８によって軸方向の移動を拘束されている。この結果、太陽歯車６はその軸方向の移動が拘束されるため、太陽歯車６とキャリア９との間の所定隙間が維持され、両者が接触することはない。このため、従来のような太陽歯車６とキャリア９の接触による磨耗が無くなるので、太陽歯車６及びキャリア９の耐久性を向上でき、故障頻度を大幅に低減できる。また、半割スペーサ４１，４１と太陽歯車６の環状溝６ｃとの間の径方向隙間は、太陽歯車６が径方向へ移動可能な所定大きさとしているため、遊星歯車７の偏荷重を受けたときの太陽歯車６の調芯性が保たれ、遊星歯車機構の荷重分担が乱れることがない。従って、遊星歯車７の偏荷重を受けても太陽歯車６はスムーズに回転でき、耐久性を向上できる。尚、半割スペーサ４１，４１は環状円盤プレートの略半分割なので、太陽歯車６の環状溝６ｃ内に容易に挿入でき、組立作業性がよい。 According to the first embodiment, the sun gear 6 is connected to the gear support shaft 23 via the half spacers 41 and 41, and the gear support shaft 23 is connected to the gear case 18 of the case 10 via the bearings 31 and 32. Axial movement is constrained. As a result, since the axial movement of the sun gear 6 is restricted, a predetermined gap between the sun gear 6 and the carrier 9 is maintained, and the sun gear 6 does not come into contact with each other. For this reason, since the abrasion by the contact of the sun gear 6 and the carrier 9 like the conventional one is eliminated, the durability of the sun gear 6 and the carrier 9 can be improved, and the failure frequency can be greatly reduced. The radial gap between the half spacers 41, 41 and the annular groove 6c of the sun gear 6 has a predetermined size that allows the sun gear 6 to move in the radial direction. The alignment of the sun gear 6 is maintained, and the load sharing of the planetary gear mechanism is not disturbed. Therefore, the sun gear 6 can rotate smoothly even if it receives an uneven load of the planetary gear 7 and the durability can be improved. Since the half spacers 41 and 41 are substantially half-divided into the annular disk plate, they can be easily inserted into the annular groove 6c of the sun gear 6 and the assembly workability is good.

次に、図２に基づき第２実施形態を説明する。図２において、図１に示す構成部材と略同一機能を有する部材には同一符号を付し、ここでの説明を省く。
第２実施形態では、入力側歯車機構１の太陽歯車６は、軸継手２３ａを介してスプライン結合により出力側歯車機構２の歯車支持軸２３と一体的に回転可能に連結されている。また、太陽歯車６のキャリア９側の端部内周部とパイプ５との間に軸受４３を設けており、この軸受４３の外輪を太陽歯車６に、内輪をキャリア９にそれぞれ当接させている。この場合、軸受４３の内部隙間は、太陽歯車６が遊星歯車７から偏荷重を受けたときに径方向に移動可能な程度の大きさに設定される。この軸受４３によって、太陽歯車６のキャリア９へ向かう方向の移動を拘束している。その他の構成は、第１実施形態と同じであるから説明を省く。 Next, a second embodiment will be described based on FIG. 2, members having substantially the same functions as those shown in FIG. 1 are denoted by the same reference numerals, and description thereof is omitted here.
In the second embodiment, the sun gear 6 of the input side gear mechanism 1 is rotatably coupled integrally with the gear support shaft 23 of the output side gear mechanism 2 by spline coupling via a shaft coupling 23a. A bearing 43 is provided between the inner peripheral portion of the sun gear 6 on the carrier 9 side and the pipe 5, and the outer ring of the bearing 43 is in contact with the sun gear 6 and the inner ring is in contact with the carrier 9. . In this case, the internal gap of the bearing 43 is set to a size that allows the sun gear 6 to move in the radial direction when the sun gear 6 receives an offset load from the planetary gear 7. The bearing 43 restrains the movement of the sun gear 6 in the direction toward the carrier 9. Since other configurations are the same as those of the first embodiment, description thereof is omitted.

第２実施形態の構成によると、軸受４３を設けたため、キャリア９に接近する方向の太陽歯車６の移動が拘束されるので、太陽歯車６はキャリア９と接触することがなく、両者間の接触による磨耗が無くなる。これにより、太陽歯車６とキャリア９の耐久性を向上でき、故障頻度を大幅に低減できる。その他の効果は、第１実施形態と同様である。   According to the structure of 2nd Embodiment, since the bearing 43 was provided, since the movement of the sun gear 6 of the direction approaching the carrier 9 is restrained, the sun gear 6 does not contact the carrier 9, but contact between both Wear due to is eliminated. Thereby, the durability of the sun gear 6 and the carrier 9 can be improved, and the failure frequency can be greatly reduced. Other effects are the same as those of the first embodiment.

次に、図３により第３実施形態を説明する。図３で、前出の図面に記載の部材と略同一機能を有する部材には同一符号を付して、ここでの説明を省く。  Next, a third embodiment will be described with reference to FIG. In FIG. 3, members having substantially the same functions as the members described in the previous drawings are denoted by the same reference numerals, and description thereof is omitted here.
入力側歯車機構１の太陽歯車６は、軸継手２３ａを介してスプライン結合等により出力側歯車機構２の歯車支持軸２３と一体的に回転可能に連結されている。また、太陽歯車６のキャリア９側端部には軸方向に突出した環状突出部６ｄを設け、この環状突出部６ｄの外周部とキャリア９の基板部１１との間に軸受４４を設けている。本例では、軸受４４の内輪を太陽歯車６の前記環状突出部６ｄの外周面に、外輪をキャリア９の基板部１１に設けた環状段差部１１ａの外周面にそれぞれ当接させている。この軸受４４によって、太陽歯車６はキャリヤ９の基板部１１へ向かう方向の移動が拘束されると共に、キャリア９に対して回転自在に支持されている。尚、他の構成は第２実施形態と同一であるため、説明を省く。  The sun gear 6 of the input side gear mechanism 1 is coupled to the gear support shaft 23 of the output side gear mechanism 2 so as to be integrally rotatable by spline coupling or the like through a shaft coupling 23a. Further, an annular projecting portion 6 d that projects in the axial direction is provided at the end of the sun gear 6 on the carrier 9 side, and a bearing 44 is provided between the outer peripheral portion of the annular projecting portion 6 d and the substrate portion 11 of the carrier 9. . In this example, the inner ring of the bearing 44 is brought into contact with the outer circumferential surface of the annular projecting portion 6 d of the sun gear 6, and the outer ring is brought into contact with the outer circumferential surface of the annular stepped portion 11 a provided on the substrate portion 11 of the carrier 9. With this bearing 44, the sun gear 6 is restrained from moving in the direction toward the substrate portion 11 of the carrier 9 and is supported rotatably with respect to the carrier 9. Since other configurations are the same as those of the second embodiment, description thereof is omitted.

第３実施形態によると、太陽歯車６は軸受４４によってキャリア９へ向かう方向の移動が拘束されるため、太陽歯車６とキャリア９との間に有する所定隙間が維持され、両者間の摺動部を無くすことができる。これにより、太陽歯車６とキャリア９との摺動による磨耗を防止できるので、耐久性を大幅に向上できる。尚、他の作用、効果は前記第２実施形態と同様であるから、その説明を省く。  According to the third embodiment, since the sun gear 6 is restrained from moving in the direction toward the carrier 9 by the bearing 44, the predetermined gap between the sun gear 6 and the carrier 9 is maintained, and the sliding portion between the two is maintained. Can be eliminated. Thereby, since the abrasion by the sliding with the sun gear 6 and the carrier 9 can be prevented, durability can be improved significantly. Since other operations and effects are the same as those of the second embodiment, description thereof is omitted.

尚、上記実施形態では、風力発電機への適用例で説明したが、本発明の適用はこれに限定されず、各種機械の遊星歯車装置にも適用可能である。   In the above embodiment, the application example to the wind power generator has been described. However, the application of the present invention is not limited to this, and the invention can be applied to planetary gear devices of various machines.

本発明の第１実施形態に係る遊星歯車装置を用いた風力発電機用増速機の側面断面図である。It is side surface sectional drawing of the step-up gearbox for wind power generators using the planetary gear apparatus which concerns on 1st Embodiment of this invention. 本発明の第２実施形態に係る遊星歯車装置を用いた風力発電機用増速機の側面断面図である。It is side surface sectional drawing of the gearbox for wind power generators using the planetary gear apparatus which concerns on 2nd Embodiment of this invention. 本発明の第３実施形態に係る遊星歯車装置を用いた風力発電機用増速機の側面断面図である。It is side surface sectional drawing of the gearbox for wind power generators using the planetary gear apparatus which concerns on 3rd Embodiment of this invention. 従来技術に係る遊星歯車装置を用いた風力発電機用増速機の側面断面図である。It is side surface sectional drawing of the gearbox for wind power generators using the planetary gear apparatus which concerns on a prior art.

符号の説明Explanation of symbols

１…入力側歯車機構、２…出力側歯車機構、４…出力軸、５…パイプ、６…太陽歯車、６ａ…筒状本体部、６ｂ…歯部、６ｃ…環状溝、７…遊星歯車、８…リングギヤ、９…キャリア、９ａ…スラスト面、１０…ケース、１１，１２…基板部、１３…円筒部、１４…連結部、１５…軸部材、１６…軸受、１７…トルクアーム、１８…ギヤケース、１９…入力軸、２０，２１…軸受、２２…外端壁、２３…歯車支持軸、２３ａ…軸継手、２３ｂ…拡径部、２４ａ，２４ｂ…スプライン（軸継手）、２５…第１歯車、２６…第２歯車、２７…軸受、２８…軸部材、２９…歯部、３０…ピニオン（ギヤ部）、３１，３２…軸受、３４…軸受、３５…側壁、３６…軸受、３７…軸継手部、４１…半割スペーサ、４２…環状プレート、４３…軸受、４４…軸受。
DESCRIPTION OF SYMBOLS 1 ... Input side gear mechanism, 2 ... Output side gear mechanism, 4 ... Output shaft, 5 ... Pipe, 6 ... Sun gear, 6a ... Cylindrical main-body part, 6b ... Tooth part, 6c ... Annular groove, 7 ... Planetary gear, DESCRIPTION OF SYMBOLS 8 ... Ring gear, 9 ... Carrier, 9a ... Thrust surface, 10 ... Case, 11, 12 ... Substrate part, 13 ... Cylindrical part, 14 ... Connection part, 15 ... Shaft member, 16 ... Bearing, 17 ... Torque arm , 18 ... Gear case , 19 ... Input shaft, 20, 21 ... Bearing, 22 ... Outer end wall, 23 ... Gear support shaft, 23a ... Shaft coupling, 23b ... Expanded diameter part, 24a, 24b ... Spline (shaft coupling), 25 ... First Gears 26 ... second gears 27 ... bearings 28 ... shaft members 29 ... tooth parts 30 ... pinions (gear parts) 31,32 ... bearings 34 ... bearings 35 ... side walls 36 ... bearings 37 ... Shaft coupling part , 41 ... half spacer, 42 ... annular plate, 43 ... bearing, 44 …bearing.

Claims (3)

遊星歯車装置の歯車締結構造において、
太陽歯車(6)の軸方向移動を拘束する拘束手段を設けた
ことを特徴とする遊星歯車装置の歯車締結構造。 In the gear fastening structure of the planetary gear device,
A gear fastening structure for a planetary gear device, characterized in that a restraining means for restraining the axial movement of the sun gear (6) is provided. 請求項１記載の遊星歯車装置の歯車締結構造において、
前記拘束手段は、
前記太陽歯車(6)の歯部(6b)の軸方向側方で筒状本体部(6a)の外周部に設けた環状溝(6c)と、
前記太陽歯車(6)の筒状本体部(6a)の外周部の外径よりも大きな外径を有する環状プレートを略半分割にして構成され、前記環状溝(6c)内に環状に配置して挿入される２つの半割スペーサ(41,41)と、
前記環状溝(6c)内に挿入した前記２つの半割スペーサ(41,41)を、前記太陽歯車(6)に一体的に回転自在に結合された歯車支持軸(23)の端面とで挟むようにして固定するプレート(42)とを備えた
ことを特徴とする遊星歯車装置の歯車締結構造。 In the gear fastening structure of the planetary gear device according to claim 1,
The restraining means is
An annular groove (6c) provided in the outer peripheral portion of the cylindrical main body (6a) on the axial side of the tooth portion (6b) of the sun gear (6);
An annular plate having an outer diameter larger than the outer diameter of the outer peripheral portion of the cylindrical main body portion (6a) of the sun gear (6) is substantially divided into two parts, and is annularly arranged in the annular groove (6c). Two halved spacers (41, 41) inserted,
The two half spacers (41, 41) inserted into the annular groove (6c) are sandwiched between end faces of a gear support shaft (23) integrally and rotatably coupled to the sun gear (6). A planetary gear device gear fastening structure, comprising: a plate (42) that is fixed in such a manner . 請求項１記載の遊星歯車装置の歯車締結構造において、
前記拘束手段は、
前記太陽歯車(6)の筒状本体部(6a)と、キャリア(9)又はキャリア(9)に固定されたパイプ(5)との間に設けた軸受(43)である
ことを特徴とする請求項１記載の遊星歯車装置の歯車締結構造。
In the gear fastening structure of the planetary gear device according to claim 1,
The restraining means is
A bearing (43) provided between the cylindrical main body (6a) of the sun gear (6) and the carrier (9) or the pipe (5) fixed to the carrier (9). The gear fastening structure of the planetary gear device according to claim 1.
JP2004041674A 2004-02-18 2004-02-18 Gear meshing structure of planetary gear device Pending JP2005233277A (en)

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Cited By (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007146666A (en) * 2005-11-24 2007-06-14 Komatsu Ltd Wind generator
CN101949445A (en) * 2009-07-09 2011-01-19 再生动力***股份公司 The transmission device of wind energy plant
WO2012127736A1 (en) * 2011-03-23 2012-09-27 住友重機械工業株式会社 Speed increasing gear for wind turbine

Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS57109352U (en) * 1981-08-11 1982-07-06
JPS5935759U (en) * 1979-03-17 1984-03-06 テイツセン・インドウストリ−・アクチエンゲゼルシヤフト planetary gearbox
JPS61175623U (en) * 1985-04-19 1986-11-01
JPS62102027U (en) * 1985-12-18 1987-06-29
JPH0771568A (en) * 1993-06-29 1995-03-17 Komatsu Ltd Bearing fixing device of epicycle reduction gear

Patent Citations (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS5935759U (en) * 1979-03-17 1984-03-06 テイツセン・インドウストリ−・アクチエンゲゼルシヤフト planetary gearbox
JPS57109352U (en) * 1981-08-11 1982-07-06
JPS61175623U (en) * 1985-04-19 1986-11-01
JPS62102027U (en) * 1985-12-18 1987-06-29
JPH0771568A (en) * 1993-06-29 1995-03-17 Komatsu Ltd Bearing fixing device of epicycle reduction gear

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2007146666A (en) * 2005-11-24 2007-06-14 Komatsu Ltd Wind generator
JP4646785B2 (en) * 2005-11-24 2011-03-09 株式会社小松製作所 Wind power generator
CN101949445A (en) * 2009-07-09 2011-01-19 再生动力***股份公司 The transmission device of wind energy plant
WO2012127736A1 (en) * 2011-03-23 2012-09-27 住友重機械工業株式会社 Speed increasing gear for wind turbine
CN103370537A (en) * 2011-03-23 2013-10-23 住友重机械工业株式会社 Speed increasing gear for wind turbine

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