JP2006097765A - Bearing support structure of rotating machine - Google Patents

Bearing support structure of rotating machine Download PDF

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Publication number
JP2006097765A
JP2006097765A JP2004283430A JP2004283430A JP2006097765A JP 2006097765 A JP2006097765 A JP 2006097765A JP 2004283430 A JP2004283430 A JP 2004283430A JP 2004283430 A JP2004283430 A JP 2004283430A JP 2006097765 A JP2006097765 A JP 2006097765A
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Prior art keywords
annular spring
bearing
annular
support structure
rotating machine
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JP2004283430A
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Japanese (ja)
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Kazuharu Ueno
一治 上野
Keiji Komatsu
恵司 小松
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Oriental Motor Co Ltd
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Oriental Motor Co Ltd
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Priority to JP2004283430A priority Critical patent/JP2006097765A/en
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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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C25/00—Bearings for exclusively rotary movement adjustable for wear or play
    • F16C25/06—Ball or roller bearings
    • F16C25/08—Ball or roller bearings self-adjusting
    • F16C25/083—Ball or roller bearings self-adjusting with resilient means acting axially on a race ring to preload the bearing
    • 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
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C19/00—Bearings with rolling contact, for exclusively rotary movement
    • F16C19/02—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows
    • F16C19/04—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly
    • F16C19/06—Bearings with rolling contact, for exclusively rotary movement with bearing balls essentially of the same size in one or more circular rows for radial load mainly with a single row or balls

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  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Support Of The Bearing (AREA)
  • Springs (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a bearing support structure of a rotating machine having an annular spring which is prevented from being deteriorated or damaged. <P>SOLUTION: In the bearing support structure of the rotating machine, the outer circumferential face in the radial direction of a bearing rotatively supporting a rotating shaft is supported on the inner circumferential face of a housing, and the end face in the axial direction of the bearing is supported on the depth end face of the housing via the annular spring having an urging force in the axial direction. An annular member 5 having a plurality of projections 7 in the axial direction formed on the plate surface is arranged between the annular spring 6 and the depth end face of the housing 4a. <P>COPYRIGHT: (C)2006,JPO&NCIPI

Description

本発明は、環状ばねの劣化や破損を防ぐことができる回転機のベアリング支持構造に関する。   The present invention relates to a bearing support structure for a rotating machine that can prevent deterioration and breakage of an annular spring.

回転機の回転軸を支持するベアリングには、通常、予圧と呼ばれる軸方向への荷重を加える。これは、ベアリングを構成する各部材間の隙間を除去し、これによりベアリング自体の剛性を確保するためである。予圧をかける方法として、環状のばねを用いるのが最も一般的である。   An axial load called preload is usually applied to the bearing that supports the rotating shaft of the rotating machine. This is to remove the gaps between the members constituting the bearing, thereby ensuring the rigidity of the bearing itself. The most common method for applying preload is to use an annular spring.

しかしながら、こうした環状ばねによる予圧のかけ方にあっては、回転機への軸方向外力、いわゆるスラスト荷重によって、環状ばねが劣化して十分な予圧が加えられなくなったり、さらにはばねが破損して全くその機能を果たさなくなるという問題があった。
このような問題を解決するため、出願人は以前、環状ばねに複数個の突起を設け、その突起によって一定の予圧を維持する方法を提案した(特許文献１参照)。
また、同様の発想による考案が、次の文献にも開示されている(特許文献２、特許文献３参照)。
特開平７−２４８０２３号公報 実開昭５７−５３１２０号公報 実開昭５３−４７４５４号公報 However, in this method of applying preload by the annular spring, the axial spring deteriorates due to the axial external force on the rotating machine, so-called thrust load, and sufficient preload is not applied or the spring is damaged. There was a problem that it could not perform its function at all.
In order to solve such problems, the applicant has previously proposed a method in which a plurality of protrusions are provided on the annular spring and a constant preload is maintained by the protrusions (see Patent Document 1).
Moreover, the idea by the same idea is also disclosed by the following literature (refer patent document 2 and patent document 3).
Japanese Patent Laid-Open No. 7-248023 Japanese Utility Model Publication No. 57-53120 Japanese Utility Model Publication No. 53-47454

しかしながら、こうした環状ばね自体に細工を施す方法は、必ずしも強度が十分ではないため長期の使用には耐えきれず、依然として上述の問題すなわち、劣化による予圧不足、そして破損といった問題が残っていた。   However, the method of crafting such an annular spring itself is not necessarily strong enough to withstand long-term use, and the above-mentioned problems, that is, insufficient preload due to deterioration, and damage remain.

本発明は、上記課題を解決し、環状ばねの劣化や破損を防ぐことができる回転機のベアリング支持構造を提供することを目的とする。   An object of the present invention is to provide a bearing support structure for a rotating machine that solves the above-described problems and can prevent deterioration and breakage of an annular spring.

本発明は、上記問題点を解決するため、回転軸を回転自在に支持するベアリングの半径方向外周面を、ハウジング部内周面に支持させるとともに、前記ベアリングの軸方向片側端面を、軸方向に付勢力を有する環状ばねを介して上記ハウジング部奥行き端面に支持させるようにした回転機のベアリング支持構造において、前記環状ばねと前記ハウジング部奥行き端面との間に、複数の軸方向の突起部を板面に設けた環状部材を配設したことにある。
また、本発明は、前記環状ばねに、円周方向に波形に形成した板ばねを用いるとともに、前記環状部材の突起部が、前記環状ばねの波形に合致するような円弧状の突起であることにある。
さらに、本発明は、前記環状部材の突起部が、前記環状ばねの疲労破壊限界高さより大きく、かつ、前記ベアリングに適性予圧をかけるための環状ばねの最小値よりも小さく構成されたことにある。
さらにまた、本発明は、前記環状部材の突起部同士の中間点の一か所に前記環状ばねを固定するための爪部を備え、前記環状ばねが前記爪部によって位置決め固定されるように構成されたことにある。 In order to solve the above problems, the present invention supports the radially outer peripheral surface of the bearing that rotatably supports the rotating shaft on the inner peripheral surface of the housing portion, and attaches one axial end surface of the bearing in the axial direction. In a bearing support structure for a rotating machine that is supported on the deep end face of the housing part via an annular spring having a force, a plurality of axial protrusions are formed between the annular spring and the deep end face of the housing part. The annular member provided on the surface is disposed.
Further, the present invention uses a leaf spring formed in a waveform in the circumferential direction for the annular spring, and the protrusion of the annular member is an arc-shaped protrusion that matches the waveform of the annular spring. It is in.
Further, according to the present invention, the protrusion of the annular member is configured to be larger than a fatigue fracture limit height of the annular spring and smaller than a minimum value of the annular spring for applying appropriate preload to the bearing. .
Furthermore, the present invention includes a claw portion for fixing the annular spring at one position of an intermediate point between the projections of the annular member, and the annular spring is positioned and fixed by the claw portion. It has been done.

本発明の効果としては、環状ばねとハウジング部奥行き端面との間に、突起部を設けた環状部材を配設することによって、環状ばねの劣化や破損を防ぐことができ、良好な回転機のベアリング支持構造を得ることができる。また、前記突起部を、前記環状ばねの波形に合致するような円弧状の突起にすることによってさらに優れたベアリング支持構造を得ることができる。また、前記突起部の高さを最適値にすることによって、さらに優れたベアリング支持構造を得ることができる。また、環状部材に設けた爪部に環状ばねを固定することによって、組み付けも容易なベアリング支持構造を得ることができる。   As an effect of the present invention, by disposing an annular member provided with a protruding portion between the annular spring and the depth end surface of the housing portion, the annular spring can be prevented from being deteriorated or damaged, and a good rotating machine A bearing support structure can be obtained. Further, an even better bearing support structure can be obtained by making the protrusions arc-like protrusions that match the waveform of the annular spring. Further, an even better bearing support structure can be obtained by optimizing the height of the protrusion. Further, by fixing the annular spring to the claw provided on the annular member, a bearing support structure that can be easily assembled can be obtained.

以下、図示の実施の形態を図面を参照しながら詳細に説明する。
図１は回転軸支持部のベアリング支持構造を示す部分断面図、図２は環状部材を示す斜視図、図３は環状ばねを示す斜視図、図４はベアリングに対する適正予圧の関係を示す図、図５（ａ）〜（ｄ）は環状ばねにかかる荷重と、その時の環状ばねの高さを示す図である。 Hereinafter, the illustrated embodiment will be described in detail with reference to the drawings.
1 is a partial cross-sectional view showing a bearing support structure of a rotating shaft support portion, FIG. 2 is a perspective view showing an annular member, FIG. 3 is a perspective view showing an annular spring, and FIG. 4 is a diagram showing a relationship of proper preload to a bearing, 5A to 5D are views showing the load applied to the annular spring and the height of the annular spring at that time.

図１は回転機の回転軸の一端部を拡大して示したもので、図１において、１は電動機、あるいは減速機等の回転機である。この回転機１の回転軸２は、半径方向外周面をベアリング３を介して回転機１のケース４内のベアリングハウジング部４ａに回転自在に支持されている。ベアリングハウジング部４ａは、ケース４内のボス部内側に形成された空洞部４１で、一定の径Ｌの側壁部４２と、奥行き端面まで所定深さＨの底壁部４３が形成されている。   FIG. 1 is an enlarged view of one end portion of a rotating shaft of a rotating machine. In FIG. 1, reference numeral 1 denotes a rotating machine such as an electric motor or a speed reducer. The rotating shaft 2 of the rotating machine 1 is rotatably supported on a bearing housing portion 4a in a case 4 of the rotating machine 1 through a bearing 3 on the outer peripheral surface in the radial direction. The bearing housing part 4a is a hollow part 41 formed inside the boss part in the case 4, and a side wall part 42 having a constant diameter L and a bottom wall part 43 having a predetermined depth H are formed up to the depth end face.

前記ベアリング３は、同心状に配置されたリング状の内輪３１と外輪３２相互間に図示しないリテイナーを介して多数のボール３３を配設したもので、内輪３１の内周面で回転軸２の端部軸部２１を支持するとともに、外輪３２の外周面をベアリングハウジング部４ａの内周面、すなわち空洞部４１の側壁部４２に支持されている。前記ベアリング３の片側端面、すなわち内輪３１と外輪３２の片側端面３１ａ，３２ａは、環状部材５と環状ばね６を介してベアリングハウジング部４ａの奥行き端面、すなわち空洞部４１の底壁部４３に支持されている。ベアリング３の内輪３１の他方側端面３１ｂは、回転軸２の端部軸部２１の基端段部２２に係止されている。   The bearing 3 has a large number of balls 33 arranged between a ring-shaped inner ring 31 and an outer ring 32 arranged concentrically via a retainer (not shown). While supporting the end shaft part 21, the outer peripheral surface of the outer ring 32 is supported by the inner peripheral surface of the bearing housing part 4a, that is, the side wall part 42 of the cavity part 41. One end surfaces of the bearing 3, that is, one end surfaces 31 a and 32 a of the inner ring 31 and the outer ring 32, are supported by the depth end surface of the bearing housing portion 4 a, that is, the bottom wall portion 43 of the cavity portion 41, via the annular member 5 and the annular spring 6. Has been. The other end surface 31 b of the inner ring 31 of the bearing 3 is locked to the proximal end step portion 22 of the end shaft portion 21 of the rotating shaft 2.

前記環状部材５と環状ばね６は、環状部材５、環状ばね６の順に空洞部４１の底壁部４３に配置されており、前記ベアリング３に対して軸方向の予圧を与えるものである。図２は環状部材５を示したもので、この環状部材５は、樹脂成形で環状に形成されたプレートで、片側板面には、円周方向に一定間隔で複数の突起部７(図示例では３箇所)が形成されている。この突起部７は円周方向に円弧状の突部を半径方向に沿って柱状に形成したものである。前記環状部材５の内周縁部には、半径方向に一対の爪部８を突設した環状のガイド用リング部９が装着されており、爪部８を介して環状ばね６を保持できるように構成されている。
前記環状ばね６は、図３に示すように、リング状の板ばねを、円周方向に沿って波状の曲面に形成して凸面部６ａを形成したもので、ベアリングハウジング部４ａの環状部材５の上に配置されて前記ベアリング３を軸方向に付勢し、ベアリング３に対して軸方向の予圧を与えるものである。 The annular member 5 and the annular spring 6 are arranged on the bottom wall 43 of the cavity 41 in the order of the annular member 5 and the annular spring 6, and apply an axial preload to the bearing 3. FIG. 2 shows an annular member 5. The annular member 5 is a plate formed in an annular shape by resin molding, and a plurality of protrusions 7 (illustrated examples) are formed on one side plate surface at regular intervals in the circumferential direction. In three places) are formed. The protrusion 7 is formed by forming an arc-shaped protrusion in the circumferential direction into a columnar shape along the radial direction. An annular guide ring portion 9 having a pair of claw portions 8 protruding in the radial direction is attached to the inner peripheral edge portion of the annular member 5 so that the annular spring 6 can be held via the claw portions 8. It is configured.
As shown in FIG. 3, the annular spring 6 is formed by forming a ring-shaped leaf spring into a wavy curved surface along the circumferential direction to form a convex surface portion 6a, and the annular member 5 of the bearing housing portion 4a. The bearing 3 is urged in the axial direction so as to apply a preload in the axial direction to the bearing 3.

次に、上記の実施の形態の作用を説明する。
空洞部４１の底壁部４３に環状部材５と環状ばね６を配置し、その上に回転軸２の端部軸部２１を支持するベアリング３を配置する。環状ばね６によりベアリング３を軸方向に付勢し、ベアリング３に対して軸方向の予圧を与える。
ベアリング３に対する適正予圧は、図４に示す関係になっており、荷重は図４に示す適正予圧範囲ｆ２−ｆ３間に保つため、環状ばね６の変形量を図４に示す範囲内ｈ２−ｈ３間で管理する必要がある。本実施の形態では、変形可能量を超える外力がスラスト方向に繰り返し加わった場合、環状ばね６が疲労破壊することのない様に環状部材５の突起部７で荷重を受けることで、環状ばね６の破損を防ぐ。環状部材５の突起部７の高さはベアリング３に対する適正予圧ｆと、バネワッシャー高さ(環状ばね６の高さ)ｈを示す図４及び図５（ａ）〜（ｄ）に示すように、バネワッシャー高さ(環状ばね６の高さ)ｈを、疲労破壊限度範囲ｈ０まで達しないｈ１に設定することで破損を防ぐ。 Next, the operation of the above embodiment will be described.
The annular member 5 and the annular spring 6 are disposed on the bottom wall portion 43 of the cavity portion 41, and the bearing 3 that supports the end shaft portion 21 of the rotating shaft 2 is disposed thereon. The bearing 3 is urged in the axial direction by the annular spring 6, and an axial preload is applied to the bearing 3.
The proper preload for the bearing 3 has the relationship shown in FIG. 4, and the load is kept between the proper preload range f2 and f3 shown in FIG. 4, so that the deformation amount of the annular spring 6 is within the range h2-h3 shown in FIG. Need to be managed between. In the present embodiment, when an external force exceeding the deformable amount is repeatedly applied in the thrust direction, the annular spring 6 is subjected to a load at the protrusion 7 of the annular member 5 so that the annular spring 6 does not undergo fatigue failure. To prevent damage. The height of the projection 7 of the annular member 5 is as shown in FIGS. 4 and 5 (a) to 5 (d) showing an appropriate preload f for the bearing 3 and a spring washer height (height of the annular spring 6) h. By setting the spring washer height (height of the annular spring 6) h to h1 which does not reach the fatigue failure limit range h0, breakage is prevented.

図６は本発明の他の実施の形態で、この場合、環状部材５の爪部８に環状ばね６を係合させて一体にして組み込んだもので、環状ばね６の凸部６ａと環状部材５の突起部７の位置を一致させる。また、環状部材５の爪部８とガイド９に組み込まれた環状ばね６は位置がずれないので、ケース４への組み込みも容易になる。   FIG. 6 shows another embodiment of the present invention. In this case, the annular spring 6 is integrally engaged with the claw portion 8 of the annular member 5, and the convex portion 6a of the annular spring 6 and the annular member are integrated. The positions of the five protrusions 7 are matched. Further, since the position of the claw portion 8 of the annular member 5 and the annular spring 6 incorporated in the guide 9 does not shift, the incorporation into the case 4 is facilitated.

以上のように、本発明の実施の形態によれば、以下に列挙する効果が得られる。
環状ばね６とベアリングハウジング部４ａの奥行き端面との間に、突起部７を設けた環状部材５を配設することによって、環状ばね６の劣化や破損を防ぐことができ、良好な回転機１のベアリング支持構造を得ることができる。また、前記突起部７を、前記環状ばね６の波形に合致するような円弧状の突起部にすることによってさらに優れたベアリング支持構造を得ることができる。また、前記突起部７の高さを最適値にすることによって、さらに優れたベアリング支持構造を得ることができる。また、環状部材６に設けた爪部８に環状ばね６を固定することによって、組み付けも容易なベアリング支持構造を得ることができる。 As described above, according to the embodiment of the present invention, the effects listed below can be obtained.
By disposing the annular member 5 provided with the projecting portion 7 between the annular spring 6 and the depth end surface of the bearing housing portion 4a, the annular spring 6 can be prevented from being deteriorated or damaged, and the excellent rotating machine 1 The bearing support structure can be obtained. In addition, an even better bearing support structure can be obtained by making the protrusion 7 an arc-shaped protrusion that matches the waveform of the annular spring 6. In addition, a more excellent bearing support structure can be obtained by optimizing the height of the protrusion 7. Further, by fixing the annular spring 6 to the claw portion 8 provided on the annular member 6, a bearing support structure that can be easily assembled can be obtained.

なお、本発明は、上記実施の形態に限定されるものではなく、例えば、環状部材５の突起部７の数は任意に設定することができる等、その他本発明の要旨を変更しない範囲内で、適宜変更して実施し得ることは言うまでもない。   In addition, this invention is not limited to the said embodiment, For example, in the range which does not change the summary of this invention, such as the number of the projection parts 7 of the annular member 5 being arbitrarily setable, etc. Needless to say, the embodiment can be appropriately changed.

本発明の実施の形態に係る回転機のベアリング支持構造を示す断面図である。It is sectional drawing which shows the bearing support structure of the rotary machine which concerns on embodiment of this invention. 図１の環状部材を示す斜視図である。It is a perspective view which shows the annular member of FIG. 図１の環状ばねを示す斜視図である。It is a perspective view which shows the annular spring of FIG. ベアリングに対する適正予圧の関係を示す図である。It is a figure which shows the relationship of the appropriate preload with respect to a bearing. （ａ）〜（ｄ）は、環状ばねにかかる荷重と、その時の環状ばねの高さを示す図である。(A)-(d) is a figure which shows the load concerning an annular spring, and the height of the annular spring at that time. 本発明の他の実施の形態に係るベアリング支持構造で、環状部材の爪に、環状ばねを固定した状態を示す斜視図である。It is a perspective view which shows the state which fixed the cyclic | annular spring to the nail | claw of the cyclic | annular member with the bearing support structure which concerns on other embodiment of this invention.

符号の説明Explanation of symbols

１ 回転機
２ 回転軸
３ ベアリング
４ ケース
４ａ ベアリングハウジング部（ハウジング部）
５ 環状部材
６ 環状ばね
７ 突起部
８ 爪部
９ ガイド用リング部
２１ 端部軸部
２２ 基端段部
４１ 空洞部
４２ 側壁部
４３ 底壁部 DESCRIPTION OF SYMBOLS 1 Rotating machine 2 Rotating shaft 3 Bearing 4 Case 4a Bearing housing part (housing part)
5 annular member 6 annular spring 7 protrusion 8 claw 9 guide ring 21 end shaft 22 base end step 41 cavity 42 side wall 43 bottom wall

Claims (4)

回転軸を回転自在に支持するベアリングの半径方向外周面を、ハウジング部内周面に支持させるとともに、前記ベアリングの軸方向片側端面を、軸方向に付勢力を有する環状ばねを介して上記ハウジング部奥行き端面に支持させるようにした回転機のベアリング支持構造において、前記環状ばねと前記ハウジング部奥行き端面との間に、複数の軸方向の突起部を板面に設けた環状部材を配設したことを特徴とする回転機のベアリング支持構造。 The outer circumferential surface of the bearing that rotatably supports the rotating shaft is supported by the inner circumferential surface of the housing portion, and the one end surface in the axial direction of the bearing is supported by an annular spring having an urging force in the axial direction. In the bearing support structure for a rotating machine that is supported on the end face, an annular member having a plurality of axial protrusions on the plate surface is disposed between the annular spring and the housing part depth end face. A bearing support structure for a rotating machine. 前記環状ばねに、円周方向に波形に形成した板ばねを用いるとともに、前記環状部材の突起部が、前記環状ばねの波形に合致するような円弧状の突起であることを特徴とする請求項１に記載の回転機のベアリング支持構造。 A leaf spring formed in a waveform in the circumferential direction is used as the annular spring, and the protrusion of the annular member is an arc-shaped protrusion that matches the waveform of the annular spring. 2. A bearing support structure for a rotating machine according to 1. 前記環状部材の突起部が、前記環状ばねの疲労破壊限界高さより大きく、かつ、前記ベアリングに適性予圧をかけるための環状ばねの最小値よりも小さく構成されたことを特徴とする請求項１または２に記載の回転機のペアリング支持構造。 The projecting portion of the annular member is configured to be larger than a fatigue fracture limit height of the annular spring and smaller than a minimum value of the annular spring for applying an appropriate preload to the bearing. 3. A pairing support structure for a rotating machine according to 2. 前記環状部材は、突起部同士の中間点の一か所に前記環状ばねを固定するための爪部を備え、前記環状ばねが前記爪部によって位置決め固定されるように構成されたことを特徴とする請求項１ないし３のいずれか１項に記載の回転機のベアリング支持構造。 The annular member is provided with a claw portion for fixing the annular spring at one position of an intermediate point between the projecting portions, and the annular spring is configured to be positioned and fixed by the claw portion. The bearing support structure for a rotating machine according to any one of claims 1 to 3.
JP2004283430A 2004-09-29 2004-09-29 Bearing support structure of rotating machine Pending JP2006097765A (en)

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Cited By (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010144782A (en) * 2008-12-17 2010-07-01 Kayaba Ind Co Ltd Biasing structure
JP2010144783A (en) * 2008-12-17 2010-07-01 Kayaba Ind Co Ltd Valve structure for shock absorber
JP2012050204A (en) * 2010-08-25 2012-03-08 Yazaki Corp Gear and instrument unit
EP3048706A1 (en) 2015-01-26 2016-07-27 Kobelco Construction Machinery Co., Ltd. Electric motor

Cited By (5)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010144782A (en) * 2008-12-17 2010-07-01 Kayaba Ind Co Ltd Biasing structure
JP2010144783A (en) * 2008-12-17 2010-07-01 Kayaba Ind Co Ltd Valve structure for shock absorber
JP2012050204A (en) * 2010-08-25 2012-03-08 Yazaki Corp Gear and instrument unit
EP3048706A1 (en) 2015-01-26 2016-07-27 Kobelco Construction Machinery Co., Ltd. Electric motor
US10014743B2 (en) 2015-01-26 2018-07-03 Kobelco Construction Machinery Co., Ltd. Electric motor

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