JP6189699B2 - Rotor core, rotor, and rotating electric machine - Google Patents

Rotor core, rotor, and rotating electric machine Download PDF

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JP6189699B2
JP6189699B2 JP2013208266A JP2013208266A JP6189699B2 JP 6189699 B2 JP6189699 B2 JP 6189699B2 JP 2013208266 A JP2013208266 A JP 2013208266A JP 2013208266 A JP2013208266 A JP 2013208266A JP 6189699 B2 JP6189699 B2 JP 6189699B2
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rotor
rotor core
shaft
fitting portion
fitting
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JP2015073387A (en
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憲生 竹田
憲生 竹田
良司 小林
良司 小林
博光 岡本
博光 岡本
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Hitachi Astemo Ltd
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Hitachi Automotive Systems Ltd
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    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K1/00—Details of the magnetic circuit
    • H02K1/06—Details of the magnetic circuit characterised by the shape, form or construction
    • H02K1/22—Rotating parts of the magnetic circuit
    • H02K1/28—Means for mounting or fastening rotating magnetic parts on to, or to, the rotor structures
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K15/00—Methods or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines
    • H02K15/02—Methods or apparatus specially adapted for manufacturing, assembling, maintaining or repairing of dynamo-electric machines of stator or rotor bodies

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Manufacturing & Machinery (AREA)
  • Iron Core Of Rotating Electric Machines (AREA)
  • Manufacture Of Motors, Generators (AREA)
  • Permanent Field Magnets Of Synchronous Machinery (AREA)

Description

本発明は、回転子鉄心、回転子、および、回転電機に関する。   The present invention relates to a rotor core, a rotor, and a rotating electrical machine.

回転電機の回転子は、電磁鋼板を軸方向に積層した回転子鉄心と、回転子鉄心と締結されたシャフトによって主に構成されている。回転電機を高速化することで、小型・軽量化が図れる。ただし、高速回転で生じる遠心力によって、回転子鉄心はシャフトから離れる方向に変形するため、回転子鉄心シャフトとの締結部には、締結力が大きく、安定した締結方法を採用しなければならない。   A rotor of a rotating electrical machine is mainly configured by a rotor core in which electromagnetic steel plates are laminated in the axial direction and a shaft fastened to the rotor core. By increasing the speed of the rotating electrical machine, the size and weight can be reduced. However, since the rotor core is deformed in a direction away from the shaft due to the centrifugal force generated by the high-speed rotation, the fastening portion with the rotor core shaft has a large fastening force and a stable fastening method must be employed.

回転子鉄心とシャフトを焼き嵌めで締結する場合、回転子鉄心の中心に円孔を設け、その円孔に丸棒のシャフトを挿入することで、シャフトの外周面と回転子鉄心が全周にわたって当接した状態での締結が可能である。一方，回転子鉄心にシャフトを圧入して両者を締結する場合、回転子鉄心に形成された円孔の中心孔に、円柱状のシャフトを圧入するには大荷重が必要である。その結果、シャフトと回転子鉄心が全周にわたって当接した状態の締結を圧入で実現するには大規模なプレス装置が必要になる。これを解決するために、回転子鉄心の中心孔とシャフトが部分的に当接するような締結方法が開示されている。   When the rotor core and the shaft are fastened by shrink fitting, a circular hole is provided in the center of the rotor core, and the shaft of the round bar is inserted into the circular hole so that the outer peripheral surface of the shaft and the rotor core extend over the entire circumference. Fastening in the contacted state is possible. On the other hand, when the shaft is press-fitted into the rotor core and fastened together, a large load is required to press-fit the cylindrical shaft into the center hole of the circular hole formed in the rotor core. As a result, a large-scale press device is required to achieve the fastening with the shaft and the rotor iron core in contact with each other by press-fitting. In order to solve this problem, a fastening method is disclosed in which the center hole of the rotor core and the shaft partially abut.

特許文献１では、回転子鉄心の中心孔の周面の周方向に所定間隔で複数の突起（図６の圧入部３１）が形成されている。特許文献２では、円柱状のシャフトを挿入する回転子鉄心の中心孔の断面形状を、正方形（図８の孔１７０）、正三角形（図１９の孔１７０）等にしている。   In Patent Document 1, a plurality of protrusions (press-fit portions 31 in FIG. 6) are formed at predetermined intervals in the circumferential direction of the peripheral surface of the center hole of the rotor core. In Patent Document 2, the cross-sectional shape of the central hole of the rotor core into which the cylindrical shaft is inserted is a square (hole 170 in FIG. 8), a regular triangle (hole 170 in FIG. 19), or the like.

特開２０１２−２３８２３号公報JP 2012-23823 A 特開２００４−１３５４６３号公報JP 2004-135463 A

シャフトを圧入し、シャフトと回転子鉄心を周方向に沿って部分的に当接させて両者を締結する方法では、シャフトと回転子鉄心の当接する部分（当接部）に圧力が発生するが、当接部の各領域で定義される圧力にばらつきが生じるという問題、すなわち、当接部において圧力分布が生じるという問題があった。   In the method in which the shaft is press-fitted and the shaft and the rotor core are partially brought into contact with each other along the circumferential direction to fasten the two, pressure is generated at the contact portion (contact portion) between the shaft and the rotor core. There is a problem that the pressure defined in each region of the contact part varies, that is, a pressure distribution occurs in the contact part.

（１）請求項１の発明による回転子鉄心は、円柱状のシャフトが圧入される中心孔と、中心孔に周方向に複数形成された嵌合部と、を備え、嵌合部は、シャフトが中心孔に圧入される際にシャフトと当接し、嵌合部の先端形状は、円弧であり、円弧の半径は、シャフトが中心孔に圧入される際にシャフトと当接する位置を含む周方向範囲において、シャフトの半径から圧入の締め代を引いた値よりも大きいことを特徴とする。
（２）請求項５の発明による回転子は、回転子鉄心と、回転子鉄心の中心孔に圧入されて一体化されているシャフトとを有し、固定子の内周側に回転可能に設けられて回転電機を構成し、回転子鉄心の中心孔にはシャフトの周面に嵌合する複数個の嵌合部が形成され、回転子鉄心は、請求項１〜４のいずれか一項に記載の回転子鉄心であることを特徴とする。
（３）請求項６の発明による回転電機は、スロットとティースを有し、ティースに巻線が巻回されてなる固定子と、固定子の内周側に回転可能に設けられ、回転子鉄心の中心孔にシャフトが圧入されてなる回転子とを有し、回転子鉄心の中心孔にはシャフトの周面に嵌合する複数個の嵌合部が形成され、回転子は、請求項５に記載の回転子であることを特徴とする。 (1) A rotor core according to the invention of claim 1 includes a center hole into which a cylindrical shaft is press-fitted, and a plurality of fitting portions formed in the circumferential direction in the center hole. When the shaft is press-fitted into the center hole, the tip shape of the fitting portion is an arc, and the radius of the arc includes the position where the shaft abuts when the shaft is press-fitted into the center hole. The range is characterized by being larger than the value obtained by subtracting the press-fit interference from the radius of the shaft .
(2) A rotor according to a fifth aspect of the present invention includes a rotor core and a shaft that is press-fitted into a central hole of the rotor core and integrated with the rotor core, and is provided rotatably on the inner peripheral side of the stator. A plurality of fitting portions that are fitted to the peripheral surface of the shaft are formed in the center hole of the rotor core, and the rotor core is defined in any one of claims 1 to 4. It is a rotor core as described.
(3) A rotating electrical machine according to the invention of claim 6 includes a stator having slots and teeth, and windings wound around the teeth, and a rotor core provided rotatably on the inner peripheral side of the stator. and a rotor central hole in the shaft is press-fitted in a plurality of fitting portions are formed to be fitted on the peripheral surface of the shaft into the center hole of the rotor core, the rotor, according to claim 5 It is a rotor as described in above.

本発明による回転子鉄心を用いることにより、高速化と強度信頼性を両立する回転子鉄心、回転子、および、回転電機を提供できる。   By using the rotor core according to the present invention, it is possible to provide a rotor core, a rotor, and a rotating electrical machine that achieve both high speed and strength reliability.

本発明の回転電機１００の構造を示す図。The figure which shows the structure of the rotary electric machine 100 of this invention. 第１実施形態の回転子２０を示す斜視図。The perspective view which shows the rotor 20 of 1st Embodiment. 第１実施形態の回転子２０の径方向断面図。A radial direction sectional view of rotor 20 of a 1st embodiment. 第１実施形態の回転子鉄心２の径方向断面図。A radial direction sectional view of rotor core 2 of a 1st embodiment. 第１実施形態の回転子鉄心２のうち、周方向４５°分を示す径方向断面図。Radial direction sectional drawing which shows the part for 45 degrees of circumferential directions among the rotor cores 2 of 1st Embodiment. 第１実施形態の回転子鉄心２の嵌合部８付近の径方向断面図。Radial direction sectional drawing of the fitting part 8 vicinity of the rotor core 2 of 1st Embodiment. 嵌合部８の先端９の圧力分布を示す図。The figure which shows the pressure distribution of the front-end | tip 9 of the fitting part 8. FIG. 回転子鉄心２の嵌合部８の先端９がシャフト５から受ける力を示す図。The figure which shows the force which the front-end | tip 9 of the fitting part 8 of the rotor core 2 receives from the shaft 5. FIG. 回転子鉄心２Ａの径方向断面図。Radial direction sectional drawing of 2 A of rotor cores. 回転子鉄心２Ｂの径方向断面図。Radial direction sectional drawing of the rotor core 2B. 回転子鉄心２Ａおよび回転子鉄心２Ｂにおける遠心力による嵌合部８の圧力変動を示す図。The figure which shows the pressure fluctuation of the fitting part 8 by the centrifugal force in 2 A of rotor cores, and the rotor core 2B. 回転子鉄心２Ｃの径方向断面図。Radial direction sectional drawing of the rotor core 2C. 回転子鉄心２Ａおよび回転子鉄心２Ｃにおける嵌合部８の圧力分布を示す図。The figure which shows the pressure distribution of the fitting part 8 in the rotor core 2A and the rotor core 2C. 第２実施形態の回転子鉄心２の径方向断面図。Radial direction sectional drawing of the rotor core 2 of 2nd Embodiment. 第３実施形態の回転子鉄心２の断面図である。It is sectional drawing of the rotor core 2 of 3rd Embodiment.

本発明における回転電機の一例として、８極１２スロット集中巻の永久磁石同期モータでの適用例を示す。しかし、本発明はこれに限定されるものではなく、他の形式のモータでも適用できる。また、本発明は、発電機などでも適用できる。   As an example of the rotating electric machine according to the present invention, an application example in an 8-pole 12-slot concentrated winding permanent magnet synchronous motor will be described. However, the present invention is not limited to this, and can be applied to other types of motors. The present invention can also be applied to a generator or the like.

――第１実施形態――
図１は、第１実施形態における回転電機１００を示す径方向断面図である。回転電機１００は、回転子２０と、回転子２０の外周側に配置された固定子３０とを備えている。符号１は回転電機１００の回転中心、すなわち、回転軸心を示している。 -First embodiment-
FIG. 1 is a radial cross-sectional view showing a rotating electrical machine 100 according to the first embodiment. The rotating electrical machine 100 includes a rotor 20 and a stator 30 disposed on the outer peripheral side of the rotor 20. Reference numeral 1 denotes the rotation center of the rotating electrical machine 100, that is, the rotation axis.

回転子２０は、回転子鉄心２と、回転子鉄心２の中心孔６に圧入される円柱状のシャフト５と、回転子鉄心２の外周側周方向に形成された磁石挿入孔３に挿入される永久磁石２１とを備えている。回転子鉄心２の中心孔６の嵌合部８は、図３〜図５によく示されているように、中心孔６に周方向に等間隔に形成されており、内周側に突出した形状を有する。シャフト５が嵌合部８の先端９に当接し、回転子鉄心２とシャフト５が締結されている。回転子鉄心２の中心孔６にシャフト５が圧入されたとき、シャフト５と嵌合部８は互いに当接しともに弾性変形するが、嵌合部８のほうがシャフト５よりも弾性変形の度合いが大きい。回転子２０を軽量化するため、回転子鉄心２の磁束の影響が及ばない領域に肉抜き孔４が周方向に等間隔に形成されている。永久磁石２１は、ネオジム磁石、サマリウムコバルト磁石、フェライト磁石などが主に用いられるが、これら以外であってもよい。   The rotor 20 is inserted into the rotor core 2, the columnar shaft 5 that is press-fitted into the center hole 6 of the rotor core 2, and the magnet insertion hole 3 that is formed in the circumferential direction on the outer periphery side of the rotor core 2. The permanent magnet 21 is provided. The fitting part 8 of the center hole 6 of the rotor core 2 is formed in the center hole 6 at equal intervals in the circumferential direction as well shown in FIGS. Has a shape. The shaft 5 abuts on the tip 9 of the fitting portion 8, and the rotor core 2 and the shaft 5 are fastened. When the shaft 5 is press-fitted into the center hole 6 of the rotor core 2, the shaft 5 and the fitting portion 8 abut against each other and elastically deform together, but the fitting portion 8 has a greater degree of elastic deformation than the shaft 5. . In order to reduce the weight of the rotor 20, the lightening holes 4 are formed at equal intervals in the circumferential direction in a region where the influence of the magnetic flux of the rotor core 2 does not reach. As the permanent magnet 21, a neodymium magnet, a samarium cobalt magnet, a ferrite magnet, or the like is mainly used, but other than these may be used.

固定子３０は、内周側周方向に形成されたティース３１と、一対のティース３１間に形成されるスロット３２と、スロット３２に挿入されティース３１に巻回される巻線３３とを備えている。巻線３３は、電力変換装置（不図示）に接続される。回転電機１００の回転子２０は、電力変換装置（不図示）から３相交流電流が固定子３０の巻線３３に通電され、回転駆動される。なお、固定子３０は、本発明が適用される種々の形態の回転電機において同様である。よって、以降では、固定子３０を省略して説明する。   The stator 30 includes a tooth 31 formed in the inner circumferential side circumferential direction, a slot 32 formed between the pair of teeth 31, and a winding 33 inserted into the slot 32 and wound around the tooth 31. Yes. Winding 33 is connected to a power converter (not shown). The rotor 20 of the rotating electrical machine 100 is driven to rotate when a three-phase alternating current is applied to the winding 33 of the stator 30 from a power converter (not shown). The stator 30 is the same in various types of rotating electrical machines to which the present invention is applied. Therefore, hereinafter, the description will be made with the stator 30 omitted.

図２は、回転子２０示す斜視図である。図３は、回転子２０の径方向断面図である。図４は、回転子鉄心２の径方向断面図である。回転子鉄心２の嵌合部８は、中心孔６に周方向に等間隔に形成されており、内周側に突出した形状を有する（図３、図４）。そして、円柱状のシャフト５が嵌合部８の先端９に当接し、回転子鉄心２とシャフト５が締結されている（図３）。さらに、磁石挿入孔３に永久磁石２１が挿入されて、回転子２０が構成される（図２、図３）。   FIG. 2 is a perspective view showing the rotor 20. FIG. 3 is a radial cross-sectional view of the rotor 20. FIG. 4 is a radial cross-sectional view of the rotor core 2. The fitting portions 8 of the rotor core 2 are formed in the center hole 6 at equal intervals in the circumferential direction and have a shape protruding toward the inner peripheral side (FIGS. 3 and 4). And the cylindrical shaft 5 contact | abuts to the front-end | tip 9 of the fitting part 8, and the rotor core 2 and the shaft 5 are fastened (FIG. 3). Further, the permanent magnet 21 is inserted into the magnet insertion hole 3 to constitute the rotor 20 (FIGS. 2 and 3).

図５〜７を用いて、嵌合部８の先端９の曲率半径によって圧力分布が変化することについて述べる。ここで、「圧力」とは、単位面積当たりの径方向の力のことを指す。また、「圧力分布」とは、先端９にかかる圧力の周方向依存性のことを指す。以下においても同様である。以下では、特に断らない限り、嵌合部８の先端９の曲率半径やシャフトの半径を圧入前の形状で表現する。これは、嵌合部８の先端９の曲率半径とシャフトの半径の議論をする際に、都合がよいからである。圧入後の形状では、嵌合部８とシャフトがともに弾性変形しており、上記の議論が難しくなる。   The change in pressure distribution depending on the radius of curvature of the tip 9 of the fitting portion 8 will be described with reference to FIGS. Here, “pressure” refers to a radial force per unit area. The “pressure distribution” refers to the circumferential direction dependency of the pressure applied to the tip 9. The same applies to the following. Hereinafter, unless otherwise specified, the radius of curvature of the tip 9 of the fitting portion 8 and the radius of the shaft are expressed by the shape before press-fitting. This is because it is convenient when discussing the radius of curvature of the tip 9 of the fitting portion 8 and the radius of the shaft. In the shape after press-fitting, both the fitting portion 8 and the shaft are elastically deformed, and the above discussion becomes difficult.

図５は、図４に示す破線で囲われた領域１１、すなわち、回転子鉄心２の周方向４５°分を拡大した図である。嵌合部８の先端９の３つのポイントについて、図示左端をＡ点，図示右端をＢ点、それらの中点をＣ点とする。以下でも同様の定義とする。第１実施形態では、シャフト５の圧入前の嵌合部８の先端９の形状は、曲率半径ｒｃの円弧となっている。ここで、圧入前のシャフトの半径をＲｓ，圧入による締め代をΔＲとすると、圧入前の状態において、円弧の中点であるＣ点から回転軸心１までの距離はＲｓ−ΔＲである。Ｒｓ−ΔＲというように、シャフト５だけが弾性変形するような表記となっているが、上述のように、シャフト５と嵌合部８はともに弾性変形する。さらに、嵌合部８のほうがシャフト５よりも弾性変形の度合いが大きい。   FIG. 5 is an enlarged view of a region 11 surrounded by a broken line shown in FIG. 4, i.e., 45 ° in the circumferential direction of the rotor core 2. Regarding the three points of the tip 9 of the fitting portion 8, the left end in the figure is the point A, the right end in the figure is the point B, and the middle point thereof is the point C. The same definition applies below. In the first embodiment, the shape of the tip 9 of the fitting portion 8 before the shaft 5 is press-fitted is an arc having a curvature radius rc. Here, assuming that the radius of the shaft before press-fitting is Rs and the allowance due to press-fitting is ΔR, in the state before press-fitting, the distance from the point C, which is the midpoint of the arc, to the rotation axis 1 is Rs−ΔR. Although only the shaft 5 is elastically deformed as Rs−ΔR, as described above, both the shaft 5 and the fitting portion 8 are elastically deformed. Further, the degree of elastic deformation of the fitting portion 8 is greater than that of the shaft 5.

図６は、嵌合部８付近を拡大した図である。嵌合部８は、回転子鉄心２の中心孔６に形成され、内周側に突出した形状となっており、内周側に形成された先端９と、周方向に対抗する側面１５を有する。先端９によってシャフト５と当接する。半径Ｒｓ−ΔＲの円弧１０を破線で示した。この円弧１０は、回転軸心１を中心として形成されている。図示されている通り、第１実施形態の回転子鉄心２の嵌合部８の先端９の曲率半径ｒｃは，Ｒｓ−ΔＲよりも大きい。すなわち、ｒｃ＞Ｒｓ−ΔＲである。   FIG. 6 is an enlarged view of the vicinity of the fitting portion 8. The fitting portion 8 is formed in the center hole 6 of the rotor core 2 and has a shape protruding toward the inner peripheral side, and has a tip 9 formed on the inner peripheral side and a side surface 15 facing the circumferential direction. . The tip 9 contacts the shaft 5. An arc 10 having a radius Rs−ΔR is indicated by a broken line. The arc 10 is formed around the rotation axis 1. As illustrated, the radius of curvature rc of the tip 9 of the fitting portion 8 of the rotor core 2 of the first embodiment is larger than Rs−ΔR. That is, rc> Rs−ΔR.

図７は、嵌合部８の先端９の曲率半径ｒｃと圧入前の先端９のＣ点から回転軸１までの距離Ｒｓ−ΔＲとの大小関係によって、嵌合部８の先端９にかかる圧力分布が変化する様子を示している。縦軸は圧力を示し、横軸は嵌合部８の先端９の位置を示す。なお、上述のように、第１実施形態の回転子鉄心２は、ｒｃ＞Ｒｓ−ΔＲとなっている。   FIG. 7 shows the pressure applied to the tip 9 of the fitting portion 8 by the magnitude relationship between the radius of curvature rc of the tip 9 of the fitting portion 8 and the distance Rs−ΔR from the point C of the tip 9 before press-fitting to the rotary shaft 1. It shows how the distribution changes. The vertical axis represents pressure, and the horizontal axis represents the position of the tip 9 of the fitting portion 8. As described above, the rotor core 2 of the first embodiment satisfies rc> Rs−ΔR.

先端９の曲率半径ｒｃが距離Ｒｓ−ΔＲと等しい場合、すなわち、ｒｃ＝Ｒｓ−ΔＲである場合、嵌合部８の先端９における圧力分布は、Ｃ点と比較してＡ点とＢ点で圧力が高い。これでは、圧入によって高い圧力となるＡ点、Ｂ点付近では、遠心力やトルクの繰返しが原因で材料に劣化が生じるため，長期間安定した締結力を実現できない。   When the radius of curvature rc of the tip 9 is equal to the distance Rs−ΔR, that is, when rc = Rs−ΔR, the pressure distribution at the tip 9 of the fitting portion 8 is at points A and B compared to point C. Pressure is high. In this case, in the vicinity of the points A and B where high pressure is caused by press-fitting, the material is deteriorated due to repeated centrifugal force and torque, so that a stable fastening force cannot be realized for a long time.

一方、第１実施形態の回転子鉄心２では、先端９の曲率半径ｒｃをＲｓ−ΔＲよりも大きく、かつ、適切な値にする（ｒｃ＞Ｒｓ−ΔＲ）ことで、先端９のＡ点およびＢ点で生じる圧力が低くなり、先端９のＡ点，Ｂ点，Ｃ点で圧力を概ね一様にすることができる。   On the other hand, in the rotor core 2 of the first embodiment, the radius of curvature rc of the tip 9 is larger than Rs−ΔR and an appropriate value (rc> Rs−ΔR), so that the point A of the tip 9 and The pressure generated at point B is reduced, and the pressure can be made substantially uniform at points A, B, and C of the tip 9.

ただし、曲率半径ｒｃを極めて大きくし、たとえば先端９の形状を直線にした場合（ｒｃ≫Ｒｓ−ΔＲ）、圧力は中点であるＣ点付近で高くなる。また、この場合、周方向端部のＡ点やＢ点ではシャフト５と当接しにくくなり、圧力が０に近づく。したがって、先端９を直線で形成することは好ましくない。   However, when the radius of curvature rc is extremely large, for example, when the shape of the tip 9 is a straight line (rc >> Rs−ΔR), the pressure becomes high in the vicinity of the middle point C. Further, in this case, it becomes difficult to come into contact with the shaft 5 at points A and B at the circumferential end, and the pressure approaches zero. Therefore, it is not preferable to form the tip 9 in a straight line.

第１実施形態の回転子２０のように ｒｃ＞Ｒｓ−ΔＲ とすることにより、嵌合部８の先端９の圧力分布が一様になれば、高圧力による材料劣化が生じる領域を低減できる。そのため、長期間安定した締結力を有する回転子鉄心２とシャフト５の圧入締結構造が実現できる。   By setting rc> Rs−ΔR as in the rotor 20 of the first embodiment, if the pressure distribution at the tip 9 of the fitting portion 8 becomes uniform, the region where material deterioration due to high pressure occurs can be reduced. Therefore, a press-fit fastening structure between the rotor core 2 and the shaft 5 having a stable fastening force for a long period can be realized.

回転電機１００の高速化を図るためには、回転子２０の許容回転速度を上げる必要がある。ロータの許容回転速度を上げるためには、回転子鉄心２とシャフト５の締め代ΔＲを大きくするなどして、圧入による回転子鉄心２とシャフト５の当接圧力を高くする必要がある。その際、先端９の曲率半径ｒｃとＲｓ−ΔＲが等しいと、先端９の周方向端部Ａ点とＢ点に生じる圧力が回転子鉄心２に使用される材料の降伏応力を超える可能性があり、容易に圧入時の締め代を大きくできない。これに対し、先端９の曲率半径ｒｃを半径（Ｒｓ−ΔＲ）より大きくして当接による圧力分布を一様にすれば、締め代の増加に伴い、Ａ点、Ｂ点、Ｃ点の圧力が一様に高くなるため、回転電機１００の高速化を目指した締め代ΔＲの増加を容易に行える。   In order to increase the speed of the rotating electrical machine 100, it is necessary to increase the allowable rotational speed of the rotor 20. In order to increase the allowable rotational speed of the rotor, it is necessary to increase the contact pressure between the rotor core 2 and the shaft 5 by press-fitting, for example, by increasing the interference ΔR between the rotor core 2 and the shaft 5. At this time, if the curvature radius rc of the tip 9 is equal to Rs−ΔR, the pressure generated at the circumferential end A and B of the tip 9 may exceed the yield stress of the material used for the rotor core 2. Yes, it is not possible to easily increase the tightening allowance during press-fitting. On the other hand, if the radius of curvature rc of the tip 9 is made larger than the radius (Rs−ΔR) and the pressure distribution due to contact is made uniform, the pressures at the points A, B, and C are increased as the tightening margin increases. Is uniformly increased, it is possible to easily increase the fastening allowance ΔR aimed at speeding up the rotating electrical machine 100.

以上の内容を数式で示すと、以下の式（１）〜（３）となる。
Ｔ ＝ ｆ ｒ ・・・（１）
ｆ ＜ Ｎ μ ｐ Ｌ１ Ｌ２ ・・・（２）
ｐ＜σｙ ・・・（３）
ここで、
Ｔは、トルク、
ｆは、回転子鉄心２のすべての嵌合部８にかかる摩擦力、
ｒは、回転子鉄心２に圧入されているときのシャフトの半径、
Ｎは、嵌合部８の数（第１実施形態の回転子鉄心２では、８個）、
μは、静止摩擦係数、
ｐは、シャフト５から受ける径方向圧力、
Ｌ１は、シャフト５からの圧力により弾性変形した際の、１個当たりの嵌合部８の先端９の周方向長さ、
Ｌ２は、回転子鉄心２の積厚、
σｙは、回転子鉄心２を構成する材料の降伏応力、
である。 When the above contents are expressed by mathematical formulas, the following formulas (1) to (3) are obtained.
T = f r (1)
f <N μ p L 1 L 2 ··· (2)
p <σ y (3)
here,
T is the torque,
f is a frictional force applied to all the fitting portions 8 of the rotor core 2;
r is the radius of the shaft when pressed into the rotor core 2;
N is the number of fitting portions 8 (eight in the rotor core 2 of the first embodiment),
μ is the coefficient of static friction,
p is the radial pressure received from the shaft 5,
L 1 is the circumferential length of the tip 9 of each fitting portion 8 when elastically deformed by the pressure from the shaft 5;
L 2 is the thickness of the rotor core 2,
σ y is the yield stress of the material constituting the rotor core 2,
It is.

なお、図８は、シャフト５（不図示）が回転子鉄心２に圧入された時の、回転子鉄心２の嵌合部８の先端９がシャフト５から受ける力を示す図である。上記パラメータのうち、ｆ、ｒ、μ、ｐ、Ｌ１、σｙが示されている。 FIG. 8 is a diagram showing the force that the tip 9 of the fitting portion 8 of the rotor core 2 receives from the shaft 5 when the shaft 5 (not shown) is press-fitted into the rotor core 2. Of the above parameters, f, r, μ, p, L 1 and σ y are shown.

上記の式（１）に示されるトルクＴは、回転子鉄心２のシャフト５に当接する嵌合部８のすべての領域において、摩擦力ｆが上記の式（２）の範囲内であれば、回転電機１００の最大トルク以上となり、シャフト５が回転子鉄心２に対してすべることはない。さらに、シャフト５から受ける径方向圧力ｐが、嵌合部８の先端９の当接面の各点において、式（３）に示す降伏応力の範囲内であれば、回転子鉄心２が塑性変形しない。すなわち、シャフト５が嵌合部８に当接による圧力分布を一様にするということは、嵌合部８の先端９の当接面の各点で定義される圧力ｐの最大値を下げることであり、圧力ｐの最大値が下がって降伏応力σｙから遠ざかるということは塑性変形しにくくなるということである。よって、その分だけ締め代ΔＲを容易に増加させることができる。 If the frictional force f is within the range of the above equation (2) in the entire region of the fitting portion 8 that contacts the shaft 5 of the rotor core 2, the torque T shown in the above equation (1) The maximum torque of the rotating electrical machine 100 is exceeded and the shaft 5 does not slide relative to the rotor core 2. Further, if the radial pressure p received from the shaft 5 is within the range of the yield stress shown in Formula (3) at each point of the contact surface of the tip 9 of the fitting portion 8, the rotor core 2 is plastically deformed. do not do. That is, making the pressure distribution due to the shaft 5 abutting against the fitting portion 8 lowers the maximum value of the pressure p defined at each point of the abutting surface of the tip 9 of the fitting portion 8. The fact that the maximum value of the pressure p decreases and moves away from the yield stress σ y means that plastic deformation becomes difficult. Therefore, the tightening allowance ΔR can be easily increased by that amount.

＜嵌合部８と肉抜き孔４に関する検討＞
第１実施形態の回転子２０の回転子鉄心２では、図４などに示す通り、嵌合部８は肉抜き孔４の径方向内側に位置しており、かつ、嵌合部８と肉抜き孔４の数は等しい。ここで、「嵌合部８が肉抜き孔４の径方向内側に位置する」ことの意味について、図４に示す回転子鉄心２の肉抜き孔４のひとつである肉抜き孔４ａと、嵌合部８のひとつである嵌合部８ａを例に取り、説明する。「嵌合部８ａが肉抜き孔４ａの径方向内側に位置する」とは、回転軸心１を通り肉抜き孔４ａと接する線分４１と線分４２で挟まれる角度θ１で示される領域でかつ肉抜き孔４ａより内周側の領域に、嵌合部８ａが位置することを意味する。以下においても同様である。なお、図４に示した第１実施形態の回転子鉄心２と同様に、後述の図９に示した回転子鉄心２Ａにおいても、嵌合部８が肉抜き孔４の径方向内側に位置する。 <Examination on fitting part 8 and lightening hole 4>
In the rotor core 2 of the rotor 20 of the first embodiment, as shown in FIG. 4 and the like, the fitting portion 8 is located on the radially inner side of the lightening hole 4, and the fitting portion 8 and the lightening are removed. The number of holes 4 is equal. Here, with respect to the meaning of “the fitting portion 8 is located on the radially inner side of the lightening hole 4”, the lightening hole 4 a which is one of the lightening holes 4 of the rotor core 2 shown in FIG. The fitting part 8a which is one of the joint parts 8 will be described as an example. “The fitting portion 8a is located on the radially inner side of the lightening hole 4a” is an area indicated by an angle θ1 that is sandwiched between the line segment 41 and the line segment 42 that are in contact with the lightening hole 4a through the rotation axis 1. And it means that the fitting part 8a is located in the area | region of the inner peripheral side from the lightening hole 4a. The same applies to the following. In addition, similarly to the rotor core 2 of the first embodiment shown in FIG. 4, also in the rotor core 2 </ b> A shown in FIG. 9, which will be described later, the fitting portion 8 is positioned on the radially inner side of the lightening hole 4. .

以下では、「嵌合部８の肉抜き孔４に対する周方向位置」および「嵌合部８の肉抜き孔４に対する数」がどのような影響を及ぼすかについて述べる。第１実施形態の回転子鉄心２は、先端９の曲率半径ｒｃがＲｓ−ΔＲよりも大きいが、以下では、第１実施形態の回転子鉄心２の代わりに、嵌合部８の先端９の曲率半径ｒｃとＲｓ−ΔＲが等しい回転子鉄心である、回転子鉄心２Ａ（図９）を基準として用いる。回転子鉄心２Ａと第１実施形態の回転子鉄心２との相違点は、先端９の曲率半径ｒｃとＲｓ−ΔＲが等しいかどうかだけであり、その他の構成は、同様であるとする。回転子鉄心２Ａの比較対象として、後述する回転子鉄心２Ｂ（図１０），回転子鉄心２Ｃ（図１２）を導入する。回転子鉄心２Ａ、回転子鉄心２Ｂ、回転子鉄心２Ｃでは、回転子鉄心２と同様に、嵌合部８が周方向に等間隔に形成される。また、肉抜き孔４も、嵌合部８と同様に、周方向に等間隔に形成される。なお、回転子鉄心２Ａ、回転子鉄心２Ｂ、回転子鉄心２Ｃにおいて、嵌合部８の先端９におけるＡ点、Ｂ点、Ｃ点の定義については、第１実施形態の回転子鉄心２と同様とする（図５、図９、図１０、図１２を参照）。   In the following, it will be described how “the circumferential position of the fitting portion 8 with respect to the lightening hole 4” and “the number of the fitting portion 8 with respect to the lightening hole 4” influence. In the rotor core 2 of the first embodiment, the radius of curvature rc of the tip 9 is larger than Rs−ΔR, but in the following, instead of the rotor core 2 of the first embodiment, the tip 9 of the fitting portion 8 The rotor core 2A (FIG. 9), which is a rotor core having the same radius of curvature rc and Rs−ΔR, is used as a reference. The only difference between the rotor core 2A and the rotor core 2 of the first embodiment is whether or not the radius of curvature rc of the tip 9 is equal to Rs−ΔR, and the other configurations are the same. As a comparison object of the rotor core 2A, a rotor core 2B (FIG. 10) and a rotor core 2C (FIG. 12) described later are introduced. In the rotor core 2 </ b> A, the rotor core 2 </ b> B, and the rotor core 2 </ b> C, like the rotor core 2, the fitting portions 8 are formed at equal intervals in the circumferential direction. Further, similarly to the fitting portion 8, the lightening holes 4 are also formed at equal intervals in the circumferential direction. In addition, in the rotor core 2A, the rotor core 2B, and the rotor core 2C, the definitions of the points A, B, and C at the tip 9 of the fitting portion 8 are the same as those of the rotor core 2 of the first embodiment. (See FIGS. 5, 9, 10, and 12).

〜嵌合部８の肉抜き孔４に対する周方向位置について〜
ここでは、肉抜き孔４と嵌合部８の数が等しいときに、嵌合部８の肉抜き孔４に対する位置が、遠心力による嵌合部８の圧力変動に及ぼす効果について述べる。嵌合部８とシャフト５が当接する際の圧力は、遠心力によって回転子鉄心２が外径側に力を受けることで変動する。この圧力変動に対しても、嵌合部８とシャフト５が当接している部分（当接部）が安定して締結力を発揮するためには、当接部の圧力分布が概ね一様であることが望ましい。 -About the circumferential position of the fitting part 8 with respect to the lightening hole 4-
Here, the effect of the position of the fitting portion 8 relative to the lightening hole 4 on the pressure fluctuation of the fitting portion 8 due to centrifugal force when the number of the lightening holes 4 and the fitting portions 8 is equal will be described. The pressure when the fitting portion 8 and the shaft 5 come into contact with each other varies when the rotor core 2 receives a force on the outer diameter side due to centrifugal force. In order for the portion where the fitting portion 8 and the shaft 5 are in contact with each other (pressure contact portion) to stably exhibit the fastening force even with this pressure fluctuation, the pressure distribution in the contact portion is substantially uniform. It is desirable to be.

図９に、回転子鉄心２Ａを示す。また、図１０に回転子鉄心２Ｂを示す。回転子鉄心２Ａ、回転子鉄心２Ｂにおいて、肉抜き孔４と嵌合部８の数は等しく、それぞれ８個である。当然ながら、この８個という具体的な数は、肉抜き孔４と嵌合部８の数が等しいという例のひとつであることは言うまでもない。以下でも同様である。   FIG. 9 shows the rotor core 2A. FIG. 10 shows the rotor core 2B. In the rotor core 2 </ b> A and the rotor core 2 </ b> B, the number of the hollow holes 4 and the fitting portions 8 are equal, and each is eight. Needless to say, the specific number of eight is one example in which the number of the lightening holes 4 and the fitting portions 8 are equal. The same applies to the following.

図９に示す回転子鉄心２Ａでは、肉抜き孔４の周方向中心１２と嵌合部の周方向中心１３が概ね一致するように配置されている。一方、図１０に示す回転子鉄心２Ｂでは、嵌合部８が肉抜き孔４の間に位置している。ここで、「嵌合部８が肉抜き孔４の間に位置する」ことの意味ついて、図１０に示す回転子鉄心２の互いに隣り合う肉抜き孔４である肉抜き孔４ｂ、４ｃと、嵌合部８のひとつである嵌合部８ｂを例に取り、説明する。まず、「肉抜き孔４の間」とは、互いに隣り合う肉抜き孔４の間（ここでは、肉抜き孔４ｂと４ｃの間）のことを意味する。そのうえで、「嵌合部８ｂが肉抜き孔４の間に位置する」とは、回転軸心１を通り肉抜き孔４ｂと接する線分４３と肉抜き孔４ｃと接する線分４４で挟まれる角度θ２で示される領域でかつ肉抜き孔４ｂおよび４ｃよりも内周側の領域に、嵌合部８ｂが位置することを意味する。以下においても同様である。   In the rotor core 2 </ b> A shown in FIG. 9, the circumferential center 12 of the lightening hole 4 and the circumferential center 13 of the fitting portion are arranged so as to substantially coincide. On the other hand, in the rotor core 2 </ b> B shown in FIG. 10, the fitting portion 8 is located between the lightening holes 4. Here, regarding the meaning of “the fitting portion 8 is located between the lightening holes 4”, the lightening holes 4 b and 4 c which are the lightening holes 4 adjacent to each other of the rotor core 2 shown in FIG. A description will be given by taking a fitting portion 8b which is one of the fitting portions 8 as an example. First, “between the lightening holes 4” means between the lightening holes 4 adjacent to each other (here, between the lightening holes 4b and 4c). In addition, “the fitting portion 8b is located between the lightening holes 4” means an angle between the line segment 43 passing through the rotation axis 1 and contacting the lightening hole 4b and the line segment 44 contacting the lightening hole 4c. This means that the fitting portion 8b is located in the region indicated by θ2 and in the region on the inner peripheral side of the lightening holes 4b and 4c. The same applies to the following.

当然ながら、上述の嵌合部８が肉抜き孔４の間に位置する位置関係では、肉抜き孔４の周方向中心１２と嵌合部の周方向中心１３が一致しない。また、嵌合部８の配置の影響だけを調べるため、回転子鉄心２Ａ同様、回転子鉄心２Ｂにおいても、嵌合部８の先端９の曲率半径ｒｃとＲｓ−ΔＲは等しく設定している。   Naturally, in the positional relationship in which the above-described fitting portion 8 is located between the lightening holes 4, the circumferential center 12 of the thinning hole 4 and the circumferential center 13 of the fitting portion do not coincide. Further, in order to examine only the influence of the arrangement of the fitting portion 8, the curvature radius rc and Rs−ΔR of the tip 9 of the fitting portion 8 are set equal in the rotor core 2 </ b> B as well as the rotor core 2 </ b> A.

図１１は、回転子鉄心２Ａを用いた回転電機１００と回転子鉄心２Ｂを用いた回転電機１００のそれぞれにおける、遠心力による嵌合部８の圧力変動の周方向依存性を示した図である。縦軸は遠心力による圧力変動を示し、横軸は嵌合部８の先端９の位置を示す。図には、２つの折れ線が描かれており、回転子鉄心２Ａ（白丸を結んだ線）と回転子鉄心２Ｂ（白四角を結んだ線）の嵌合部８の先端９における圧力分布を示している。先端９のほとんどすべての領域において、回転子鉄心２Ｂの圧力分布を示す折れ線のほうが、回転子鉄心２Ａのそれよりも遠心力による圧力変動が高くなっている。このことから、肉抜き孔４の径方向内側に嵌合部８を形成することにより、遠心力による嵌合部８の圧力変動が小さくなることがわかる。なお、先端９の曲率半径ｒｃをＲｓ−ΔＲよりも大きくした第１実施形態の回転子鉄心２においても、上述した比較をした場合、同様の結果が得られている。   FIG. 11 is a diagram illustrating the circumferential dependence of pressure fluctuations of the fitting portion 8 due to centrifugal force in each of the rotating electrical machine 100 using the rotor core 2A and the rotating electrical machine 100 using the rotor core 2B. . The vertical axis represents pressure fluctuation due to centrifugal force, and the horizontal axis represents the position of the tip 9 of the fitting portion 8. In the figure, two broken lines are drawn, and the pressure distribution at the tip 9 of the fitting portion 8 of the rotor core 2A (line connecting white circles) and the rotor core 2B (line connecting white squares) is shown. ing. In almost all regions of the tip 9, the broken line indicating the pressure distribution of the rotor core 2B has a higher pressure fluctuation due to centrifugal force than that of the rotor core 2A. From this, it can be seen that by forming the fitting portion 8 on the radially inner side of the lightening hole 4, the pressure fluctuation of the fitting portion 8 due to centrifugal force is reduced. In the rotor core 2 of the first embodiment in which the curvature radius rc of the tip 9 is larger than Rs−ΔR, the same result is obtained when the above comparison is made.

〜嵌合部８の肉抜き孔４に対する数について〜
ここでは、嵌合部８の肉抜き孔４に対する数が、シャフト５と当接する嵌合部８の先端９における圧力分布に及ぼす効果について述べる。回転子鉄心２Ａでは、肉抜き孔４と嵌合部８の数が等しく、両者ともに８個である（図４を参考のこと）。後述する図１３（ａ）の説明のため、図９に示す回転子鉄心２Ａが有する８個の等価な嵌合部８のうちの２個に嵌合部８ａ、嵌合部８ｂと符号を付し直した。 -About the number with respect to the lightening hole 4 of the fitting part 8-
Here, the effect of the number of the fitting portions 8 with respect to the lightening holes 4 on the pressure distribution at the tip 9 of the fitting portion 8 that abuts the shaft 5 will be described. In the rotor core 2A, the number of the lightening holes 4 and the fitting portions 8 are equal, and both are eight (see FIG. 4). For the description of FIG. 13A to be described later, two of the eight equivalent fitting portions 8 included in the rotor core 2A shown in FIG. 9 are denoted with the fitting portions 8a and 8b. Reworked.

図１２に示す回転子鉄心２Ｃでは、嵌合部８と肉抜き孔４の数が異なるものになっている。具体的には、嵌合部８が１０個、肉抜き孔４が８個形成されている。なお、後述する図１３（ｂ）の説明のため、図１２に示す回転子鉄心２Ｃが有する１０個の嵌合部８のうちの３個に嵌合部８ｃ、嵌合部８ｄ、嵌合部８ｅと符号を付し直した。嵌合部８ｃは、全体が肉抜き孔４の径方向内側に位置している。嵌合部８ｄは、Ａ点側の約半分が肉抜き孔４の径方向内側に位置しており、Ｂ点側の約半分が肉抜き孔４の間に位置している。嵌合部８ｅは、全体が肉抜き孔４の間に位置している。以上のような嵌合部８ｃ〜８ｅの非等価性が、シャフト５と当接する嵌合部８の先端９における圧力分布に影響する。詳細は図１３（ｂ）を用いて後述する。   In the rotor core 2 </ b> C shown in FIG. 12, the numbers of the fitting portions 8 and the lightening holes 4 are different. Specifically, ten fitting portions 8 and eight lightening holes 4 are formed. For the description of FIG. 13B described later, three of the ten fitting portions 8 included in the rotor core 2C shown in FIG. 12 include three fitting portions 8c, fitting portions 8d, and fitting portions. The code was re-assigned to 8e. The entire fitting portion 8 c is located on the radially inner side of the lightening hole 4. In the fitting portion 8 d, about half of the point A side is located on the radially inner side of the lightening hole 4, and about half of the point B side is located between the lightening holes 4. The entire fitting portion 8 e is located between the lightening holes 4. The non-equivalence of the fitting portions 8 c to 8 e as described above affects the pressure distribution at the tip 9 of the fitting portion 8 that contacts the shaft 5. Details will be described later with reference to FIG.

図１３（ａ）は、図９に示す回転子鉄心２Ａを用いた回転電機１００において、シャフト５と当接する、回転子鉄心２の嵌合部８の先端９における圧力分布、およびその圧力分布の嵌合部依存性を示した図である。縦軸は圧力を示し、横軸は嵌合部８の先端９の位置を示す。図１３（ａ）には、２本の折れ線が示されている。これは、図９に示す回転子鉄心２Ａの嵌合部８である嵌合部８ａ（白丸を結んだ線）と嵌合部８ｂ（黒丸を結んだ線）の先端９における圧力分布を示している。嵌合部８ａ、嵌合部８ｂのそれぞれの先端９における圧力分布を示す上述の２本の折れ線はほぼ重なり、同様の圧力分布を示すことが分かる。これは、回転子鉄心２Ａの嵌合部８が、肉抜き孔４と数が等しく、かつ、周方向に等間隔に形成されているため、嵌合部８ａと嵌合部８ｂが肉抜き孔４の位置に対して等価となっているからである。   FIG. 13A shows the pressure distribution at the tip 9 of the fitting portion 8 of the rotor core 2 that contacts the shaft 5 and the pressure distribution in the rotating electrical machine 100 using the rotor core 2A shown in FIG. It is the figure which showed the fitting part dependence. The vertical axis represents pressure, and the horizontal axis represents the position of the tip 9 of the fitting portion 8. FIG. 13A shows two broken lines. This shows the pressure distribution at the tip 9 of the fitting part 8a (line connecting white circles) and the fitting part 8b (line connecting black circles) which are the fitting parts 8 of the rotor core 2A shown in FIG. Yes. It can be seen that the above-mentioned two broken lines showing the pressure distribution at the respective tips 9 of the fitting portion 8a and the fitting portion 8b almost overlap and show the same pressure distribution. This is because the fitting portions 8 of the rotor core 2A have the same number as the lightening holes 4 and are formed at equal intervals in the circumferential direction, so that the fitting portions 8a and the fitting portions 8b are the lightening holes. This is because it is equivalent to the position of 4.

図１３（ｂ）は、図１２に示す回転子鉄心２Ｃを用いた回転電機１００において、シャフト５と当接する、回転子鉄心２の嵌合部８である嵌合部８ｃ、嵌合部８ｄ、嵌合部８ｅのそれぞれの先端９における圧力分布、およびその圧力分布の嵌合部依存性を示した図である。縦軸は圧力を示し、横軸は嵌合部８の先端９の位置を示す。図１３（ｂ）には、３本の折れ線が示されている。これは、図１２に示す回転子鉄心２Ｃの嵌合部８である嵌合部８ｃ（白丸を結んだ線）、嵌合部８ｄ（黒丸を結んだ線）、嵌合部８ｅ（白四角を結んだ線）の先端９における圧力分布を示している。嵌合部８ｃ〜８ｅのそれぞれの先端９における圧力分布を示す上述の３本の折れ線が重なっていないことから、嵌合部８ｃ〜８ｅで圧力分布が等しくないことがわかる。これは、回転子鉄心２Ｃの嵌合部８が、肉抜き孔４と数が異なり、かつ、周方向に等間隔に形成されているためである。   FIG. 13B shows a fitting portion 8c, a fitting portion 8d, which is a fitting portion 8 of the rotor core 2 that comes into contact with the shaft 5, in the rotating electrical machine 100 using the rotor core 2C shown in FIG. It is the figure which showed the pressure distribution in each front-end | tip 9 of the fitting part 8e, and the fitting part dependence of the pressure distribution. The vertical axis represents pressure, and the horizontal axis represents the position of the tip 9 of the fitting portion 8. FIG. 13B shows three broken lines. This includes a fitting portion 8c (line connecting white circles), a fitting portion 8d (line connecting black circles), and a fitting portion 8e (white squares) which are the fitting portions 8 of the rotor core 2C shown in FIG. The pressure distribution at the tip 9 of the connected line) is shown. Since the above-mentioned three broken lines showing the pressure distribution at the respective tips 9 of the fitting portions 8c to 8e do not overlap, it can be seen that the pressure distributions are not equal in the fitting portions 8c to 8e. This is because the number of the fitting portions 8 of the rotor core 2C is different from that of the lightening holes 4 and is formed at equal intervals in the circumferential direction.

このように、回転子鉄心２Ａでは嵌合部８のそれぞれの間で圧力に差がなく、長期的に信頼性の高い回転子鉄心２とシャフト５の締結が実現される。なお、先端９の曲率半径ｒｃをＲｓ−ΔＲよりも大きくした回転子鉄心である、第１実施形態の回転子鉄心２において、上述した比較をした場合でも、同様の結果が得られている。   As described above, in the rotor core 2A, there is no difference in pressure between the respective fitting portions 8, and the rotor core 2 and the shaft 5 that are highly reliable in the long term are realized. In the rotor core 2 of the first embodiment, which is the rotor core having the curvature radius rc of the tip 9 larger than Rs−ΔR, the same result is obtained even when the above-described comparison is made.

上述した「嵌合部８の肉抜き孔４に対する周方向位置が、嵌合部８における圧力変動に及ぼす効果」や、「嵌合部８の肉抜き孔４に対する数が、シャフト５と当接する回転子鉄心２の嵌合部８の先端９における圧力分布に及ぼす効果」は、以下に示す第２実施形態や第３実施形態においても同様に奏することができる。   As described above, “the effect of the circumferential position of the fitting portion 8 with respect to the lightening hole 4 on the pressure fluctuation in the fitting portion 8” and “the number of the fitting portion 8 with respect to the lightening hole 4 abuts on the shaft 5. The “effect on the pressure distribution at the tip 9 of the fitting portion 8 of the rotor core 2” can be similarly achieved in the second and third embodiments described below.

――第２実施形態――
図１４は、第２実施形態の回転電機１００の回転子２０の回転子鉄心２の嵌合部８付近の径方向断面図である。第２実施形態においても嵌合部８の先端９は円弧であるが、第１実施形態とは異なり、円弧の曲率半径ｒｃは、半径Ｒｓ−ΔＲ（図５、図６を参考のこと）と等しい。すなわち、ｒｃ＝Ｒｓ−ΔＲである。そして、嵌合部８の周方向側面１５に切欠き１４が形成されている。上述のように、先端９の曲率半径ｒｃをＲｓ−ΔＲと等しくした場合、シャフト５と当接する先端９の端部Ａ点とＢ点における圧入による圧力が中点のＣ点より高くなる。そこで、第２実施形態では、先端９の曲率半径ｒｃと半径Ｒｓ−ΔＲを上述のように等しくしたうえで、さらに、切欠き１４を側面１５に設けた。これにより、端部Ａ点とＢ点付近における嵌合部８の剛性が低減されるため、シャフト５の圧入時における端部Ａ点、Ｂ点での圧力上昇が低減される。このように、第２実施形態でも第１実施形態と同様に、シャフト５と当接する回転子鉄心２の嵌合部８の先端９における圧力分布を一様化する効果があり、長期にわたって安定した締結を実現できる。 -Second embodiment-
FIG. 14 is a radial cross-sectional view of the vicinity of the fitting portion 8 of the rotor core 2 of the rotor 20 of the rotating electrical machine 100 of the second embodiment. Also in the second embodiment, the tip 9 of the fitting portion 8 is an arc, but unlike the first embodiment, the radius of curvature rc of the arc is a radius Rs−ΔR (see FIGS. 5 and 6). equal. That is, rc = Rs−ΔR. A notch 14 is formed in the circumferential side surface 15 of the fitting portion 8. As described above, when the radius of curvature rc of the tip 9 is equal to Rs−ΔR, the pressure due to the press-fitting at the end A point and the B point of the tip 9 contacting the shaft 5 becomes higher than the C point at the middle point. Therefore, in the second embodiment, the curvature radius rc and the radius Rs−ΔR of the tip 9 are made equal as described above, and the notch 14 is further provided on the side surface 15. Thereby, since the rigidity of the fitting part 8 in the vicinity of the end A point and the B point is reduced, a pressure increase at the end A point and the B point when the shaft 5 is press-fitted is reduced. As described above, the second embodiment also has the effect of uniformizing the pressure distribution at the tip 9 of the fitting portion 8 of the rotor core 2 in contact with the shaft 5, as in the first embodiment, and is stable over a long period of time. Fastening can be realized.

――第３実施形態――
図１５は、第３実施形態の回転電機１００の回転子２０の嵌合部８付近の径方向断面図である。第３実施形態では、嵌合部８の先端９の形状は円弧ではなく、以下のような条件を満たすスプライン曲線となっている。例えば、図１５のように、先端９を周方向に等間隔に分割する点１６を考え、圧入によって先端９に生じる圧力分布が一様となるように点１６を径方向に移動させる。このようにして配置した点１６を滑らかにつなぐスプライン曲線によって、先端９が形成される。これによって、第３実施形態でも第１実施形態や第２実施形態と同様に、シャフト５と当接する回転子鉄心２の嵌合部８の先端９における圧力分布を一様化する効果を奏し、長期にわたって安定した締結を実現できる。 -Third embodiment-
FIG. 15 is a radial cross-sectional view of the vicinity of the fitting portion 8 of the rotor 20 of the rotating electrical machine 100 of the third embodiment. In 3rd Embodiment, the shape of the front-end | tip 9 of the fitting part 8 is not a circular arc but the spline curve which satisfy | fills the following conditions. For example, as shown in FIG. 15, a point 16 that divides the tip 9 at equal intervals in the circumferential direction is considered, and the point 16 is moved in the radial direction so that the pressure distribution generated at the tip 9 by press fitting becomes uniform. The tip 9 is formed by a spline curve that smoothly connects the points 16 arranged in this manner. As a result, in the third embodiment as well, as in the first and second embodiments, the pressure distribution at the tip 9 of the fitting portion 8 of the rotor core 2 that comes into contact with the shaft 5 is uniformed. A stable fastening can be realized over a long period of time.

以上の実施形態においては、回転子鉄心２の嵌合部８や、肉抜き孔４を周方向に等間隔に配置したが、本発明の趣旨に反しない範囲で等間隔でない配置にすることも可能である。   In the above embodiment, the fitting portions 8 of the rotor core 2 and the lightening holes 4 are arranged at equal intervals in the circumferential direction, but may be arranged at non-equal intervals as long as they do not contradict the gist of the present invention. Is possible.

以上の実施形態における回転電機としてモータの例を示したが、本発明は発電機などにおいても適用できる。   Although an example of a motor is shown as the rotating electrical machine in the above embodiment, the present invention can also be applied to a generator or the like.

以上の説明はあくまで一例であり、発明は、以上の実施形態に何ら限定されるものではない。   The above description is merely an example, and the present invention is not limited to the above embodiment.

１…回転軸、 ２…回転子鉄心、 ３…永久磁石の挿入孔、 ４…肉抜き孔、
５…シャフト、 ６…回転子鉄心の中心孔、
８…回転子鉄心とシャフトの嵌合部、 ９…嵌合部の先端、
１０…半径Ｒｓ−ΔＲの円弧、 １１…回転子鉄心の周方向４５゜分の領域、
１２…肉抜き孔の周方向中心、 １３…嵌合部の周方向中心、
１４…嵌合部側面の切欠き、 １５…嵌合部の側面、 １６…嵌合部先端の分割点、
２０…回転子（ロータ）、 ２１…永久磁石、 ３０…固定子（ステータ）、
３１…ティース、 ３２…スロット、 ３３…巻線、 １００…回転電機、
Ｔ…トルク、 ｆ…摩擦力、 ｒ…圧入時のシャフトの半径、
Ｎ…嵌合部８の数、 μ…静止摩擦係数、 ｐ…圧力、
Ｌ１…嵌合部先端の周方向長さ、 Ｌ２…積厚、 σｙ…降伏応力
DESCRIPTION OF SYMBOLS 1 ... Rotating shaft, 2 ... Rotor core, 3 ... Permanent magnet insertion hole, 4 ... Meat removal hole,
5 ... Shaft 6 ... Center hole of rotor core,
8: The fitting portion of the rotor core and the shaft, 9 ... The tip of the fitting portion,
10: Arc of radius Rs-ΔR, 11: Area of 45 ° in the circumferential direction of the rotor core,
12 ... Center in the circumferential direction of the hole, 13 ... Center in the circumferential direction of the fitting portion,
14 ... Notch on the side surface of the fitting part, 15 ... Side surface of the fitting part, 16 ... Division point at the tip of the fitting part,
20 ... Rotor (rotor), 21 ... Permanent magnet, 30 ... Stator (stator),
31 ... Teeth, 32 ... Slot, 33 ... Winding, 100 ... Rotating electric machine,
T: Torque, f: Friction force, r ... Shaft radius when press-fitted,
N: number of fitting portions 8, μ: coefficient of static friction, p: pressure,
L 1 ... circumferential length at the tip of the fitting part, L 2 ... thickness, σ y ... yield stress

Claims (6)

円柱状のシャフトが圧入される中心孔と、
前記中心孔に周方向に複数形成された嵌合部と、を備え、
前記嵌合部は、前記シャフトが前記中心孔に圧入される際に前記シャフトと当接する回転子鉄心において、
前記嵌合部の先端形状は、円弧であり、
前記円弧の半径は、前記シャフトが前記中心孔に圧入される際に前記シャフトと当接する位置を含む周方向範囲において、前記シャフトの半径から前記圧入の締め代を引いた値よりも大きい回転子鉄心。 A central hole into which a cylindrical shaft is press-fitted, and
A plurality of fitting portions formed in the circumferential direction in the center hole,
In the rotor core that contacts the shaft when the shaft is press-fitted into the center hole,
The tip shape of the fitting portion is an arc,
The radius of the circular arc is larger than a value obtained by subtracting the press-fit interference from the radius of the shaft in a circumferential range including a position where the shaft comes into contact with the shaft when the shaft is press-fitted into the center hole. Iron core. 請求項１に記載の回転子鉄心において、
周方向に形成された複数の肉抜き孔をさらに備え、
前記嵌合部は、前記肉抜き孔の径方向内側に形成される回転子鉄心。 The rotor core according to claim 1 ,
It further comprises a plurality of lightening holes formed in the circumferential direction,
The fitting portion is a rotor core formed on the radially inner side of the lightening hole. 請求項２に記載の回転子鉄心において、
前記嵌合部および前記肉抜き孔は、前記肉抜き孔と前記嵌合部の周方向中心が概ね一致するように形成される回転子鉄心。 In the rotor core according to claim 2 ,
The fitting portion and the lightening hole are rotor cores formed so that a center in a circumferential direction of the lightening hole and the fitting portion substantially coincides with each other. 請求項２または３に記載の回転子鉄心において、
前記嵌合部と同数の前記肉抜き孔を備える回転子鉄心。 In the rotor core according to claim 2 or 3 ,
A rotor core provided with the same number of the hollow holes as the fitting portions . 回転子鉄心と、前記回転子鉄心の中心孔に圧入されて一体化されているシャフトとを有し、固定子の内周側に回転可能に設けられて回転電機を構成し、前記回転子鉄心の中心孔には前記シャフトの周面に嵌合する複数個の嵌合部が形成されている回転子において、
前記回転子鉄心は、請求項１〜４のいずれか一項に記載の回転子鉄心である回転子。 A rotor iron core and a shaft that is press-fitted into and integrated with a central hole of the rotor iron core, and is rotatably provided on the inner peripheral side of the stator to constitute a rotating electric machine; In the rotor in which a plurality of fitting portions that are fitted to the peripheral surface of the shaft are formed in the center hole of
The said rotor iron core is a rotor which is a rotor iron core as described in any one of Claims 1-4 . スロットとティースを有し、ティースに巻線が巻回されてなる固定子と、
前記固定子の内周側に回転可能に設けられ、回転子鉄心の中心孔にシャフトが圧入されてなる回転子とを有し、前記回転子鉄心の中心孔には前記シャフトの周面に嵌合する複数個の嵌合部が形成されている回転電機において、
前記回転子は、請求項５に記載の回転子である回転電機。
A stator having slots and teeth, and windings wound around the teeth;
A rotor provided rotatably on the inner peripheral side of the stator and having a shaft press-fitted into a center hole of the rotor core, and fitted into a peripheral surface of the shaft in the center hole of the rotor core. In a rotating electrical machine in which a plurality of mating portions are formed,
The rotating electric machine according to claim 5 , wherein the rotor is a rotor according to claim 5 .
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