JP5921417B2

JP5921417B2 - Rotating electric machine

Info

Publication number: JP5921417B2
Application number: JP2012248048A
Authority: JP
Inventors: 孝明長嶋; 川崎　亮; 亮川崎; 正夫成田; 航治川嶋
Original assignee: Mitsubishi Electric Corp
Current assignee: Mitsubishi Electric Corp
Priority date: 2012-11-12
Filing date: 2012-11-12
Publication date: 2016-05-24
Anticipated expiration: 2032-11-12
Also published as: JP2014096951A

Description

この発明は、回転子の回転運動に起因する振動を低減させるために設置された動吸振器を有する回転電機に関するものである。 The present invention relates to a rotating electrical machine having a dynamic vibration absorber installed in order to reduce vibration caused by rotational movement of a rotor.

回転電機は、回転軸を有する回転子と、回転子の外周を囲うように設置された固定子と、固定子を覆うように構成された筐体と、固定子を支持するために固定子と筐体間に配置された固定子支持部材を有する。回転電機では、回転子の回転運動に伴って発生した電磁加振力が回転子と固定子に作用する。この電磁加振力が主な原因となり、固定子が振動する。このとき、固定子は振動モードと呼ばれる固有の形状で振動する。また、その振動モードの形状は多くの周波数のものがある。 The rotating electrical machine includes a rotor having a rotating shaft, a stator installed so as to surround an outer periphery of the rotor, a casing configured to cover the stator, a stator for supporting the stator, A stator support member disposed between the housings; In a rotating electrical machine, an electromagnetic excitation force generated with the rotational movement of the rotor acts on the rotor and the stator. This electromagnetic excitation force is the main cause and the stator vibrates. At this time, the stator vibrates in a unique shape called a vibration mode. Further, the vibration mode has many shapes.

固定子の半径方向の振動に注目した場合、各振動モードにおいて、半径方向の最大振幅点は腹、半径方向の振幅０の点は節と呼ばれる。回転磁界の発生と共に電磁加振力も回転するため、固定子上の固定子支持部材の取り付け位置では、固定子の半径方向振動の腹と節が交互に発生する。この固定子の振動が固定子支持部材を介して筐体に伝達され、筐体から振動と騒音が発生するという問題があった。 When attention is paid to the radial vibration of the stator, in each vibration mode, the maximum point in the radial direction is called an antinode and the point having zero amplitude in the radial direction is called a node. Since the electromagnetic excitation force also rotates with the generation of the rotating magnetic field, antinodes and nodes of the radial vibration of the stator are alternately generated at the attachment position of the stator support member on the stator. The vibration of the stator is transmitted to the casing through the stator support member, and there is a problem that vibration and noise are generated from the casing.

この問題に対して、固定子に動吸振器を取り付け、動吸振器の力を固定子に加えることによって固定子の振動を抑振することができる。 To solve this problem, the vibration of the stator can be suppressed by attaching a dynamic vibration absorber to the stator and applying the force of the dynamic vibration absorber to the stator.

従来の発明では、固定子上の固定子支持部材の取り付け位置が振動の腹となる振動モードに対してこの振動モードの腹となる位置に固定子の半径方向に振動するように動吸振器を固定子の周囲に設置し、固定子の振動を制御することにより、固定子上の固定子支持部材の取り付け位置を半径方向振動の節付近にすることによって回転電機の振動を抑振する技術が提案されている（例えば、特許文献１参照）。 In the conventional invention, the dynamic vibration absorber is arranged to vibrate in the radial direction of the stator at the position where the attachment position of the stator support member on the stator becomes the antinode of the vibration mode. There is a technology that suppresses the vibration of the rotating electrical machine by installing it around the stator and controlling the vibration of the stator so that the mounting position of the stator support member on the stator is near the radial vibration node. It has been proposed (see, for example, Patent Document 1).

特開平２０１０−１２４５９１号公報（第８頁、図２）Japanese Unexamined Patent Publication No. 2010-124591 (8th page, FIG. 2)

一般に、動吸振器の質量を増加させることと、半径方向振動の腹に動吸振器を設置することで、動吸振器の高い制振効果を得ることが可能である。上記特許文献１は、動吸振器の高い制振効果を得るための手段として、半径方向振動の腹付近で固定子の半径方向に振動するように設置された動吸振器を回転電機に適用するものである。この構成によれば、動吸振器が固定子上の固定子支持部材の取り付け位置が腹となる振動を低減させ、筐体に伝達する振動を抑制することが可能である。しかし、例えば、振動モードの腹付近に冷却器が設けられるなど、回転電機の構造が制約されると、振動モードの腹付近に動吸振器を設置することが困難となるという問題があった。 Generally, it is possible to obtain a high vibration damping effect of the dynamic vibration absorber by increasing the mass of the dynamic vibration absorber and installing the dynamic vibration absorber on the antinode of radial vibration. In Patent Document 1, as a means for obtaining a high vibration damping effect of a dynamic vibration absorber, a dynamic vibration absorber installed to vibrate in the radial direction of the stator near the antinode of radial vibration is applied to a rotating electrical machine. Is. According to this configuration, it is possible for the dynamic vibration absorber to reduce vibrations where the attachment position of the stator support member on the stator becomes an antinode, and to suppress vibrations transmitted to the housing. However, if the structure of the rotating electrical machine is restricted, for example, a cooler is provided near the antinode of the vibration mode, there is a problem that it becomes difficult to install the dynamic vibration absorber near the antinode of the vibration mode.

また、振動モードの腹の位置に動吸振器を設置することができても、固定子と筐体との間の空間が狭いといった回転電機の構造の場合、動吸振器の大きさ、つまり質量が制限されるため、十分な制振効果を得ることができないという問題があった。 In the case of a rotating electrical machine structure where the space between the stator and the housing is narrow even if the dynamic vibration absorber can be installed at the antinode position of the vibration mode, the size of the dynamic vibration absorber, that is, the mass However, there is a problem that a sufficient vibration control effect cannot be obtained.

この発明は、上記のような問題点を解決するためになされたものであり、上記のような構造上の制約がある回転電機に対して、回転電機の振動を低減する動吸振器の設置位置の自由度を上げることを目的としている。 The present invention has been made to solve the above-described problems, and the installation position of the dynamic vibration absorber that reduces the vibration of the rotating electrical machine with respect to the rotating electrical machine having the structural constraints as described above. The purpose is to increase the degree of freedom.

本発明に係る回転電機は、回転子と、上記回転子の外周を囲むように配置された固定子と、上記固定子の外周を覆う筐体と、上記固定子を、上記固定子の外周の面と上記筐体との間に、取り付け位置で支持する弾性部材からなる固定子支持部材と、弾性変形する第１弾性部と上記第１弾性部の一端に取り付けられた第１質量部とを有し、上記第１弾性部の他端が上記固定子に固定されるようにした第１動吸振器とを有し、上記固定子支持部材の取り付け位置が上記固定子の半径方向の振動の腹となり、上記固定子支持部材の取り付け位置から上記固定子の周方向に４５度移動した位置が上記半径方向の振動の節となる第１楕円振動モード、及び上記固定子支持部材の取り付け位置が上記半径方向の振動の節となり、上記固定子支持部材の取り付け位置から周方向に４５度移動した位置が上記半径方向の振動の腹となる第２楕円振動モードが発生する回転電機おいて、
上記第１質量部が上記固定子の周方向に振動するように構成した上記第１動吸振器を、上記第１楕円振動モードの節の位置または上記第２楕円振動モードの節の位置に配設し、上記第１動吸振器は、上記第１弾性部が板ばねからなり、同じ長さと幅の２つの上記第１弾性部で上記第１弾性部の幅と同じ厚さを有する上第１記質量部を挟持してなるものである。
また、回転子と、上記回転子の外周を囲むように配置された固定子と、上記固定子の外周を覆う筐体と、上記固定子を、上記固定子の外周の面と上記筐体との間に、取り付け位置で支持する弾性部材からなる固定子支持部材と、弾性変形する第１弾性部と上記第１弾性部の一端に取り付けられた第１質量部とを有し、上記第１弾性部の他端が上記固定子に固定されるようにした第１動吸振器とを有し、上記固定子支持部材の取り付け位置が上記固定子の半径方向の振動の腹となり、上記固定子支持部材の取り付け位置から上記固定子の周方向に４５度移動した位置が上記半径方向の振動の節となる第１楕円振動モード、及び上記固定子支持部材の取り付け位置が上記半径方向の振動の節となり、上記固定子支持部材の取り付け位置から周方向に４５度移動した位置が上記半径方向の振動の腹となる第２楕円振動モードが発生する回転電機おいて、
上記第１質量部が上記固定子の周方向に振動するように構成した上記第１動吸振器を、上記第１楕円振動モードの節の位置または上記第２楕円振動モードの節の位置に配設し、
上記第１動吸振器を上記第１楕円振動モードの節に配設した場合には上記第１楕円振動モードの腹の位置に、上記第１動吸振器を上記第２楕円振動モードの節に配設した場合には上記第２楕円振動モードの腹の位置に、弾性変形する第２弾性部と上記第２弾性部の一端に取り付けられた第２質量部とを有する第２動吸振器を、上記第２質量部が上記固定子の半径方向に振動するように上記固定子に設置し、
上記第２動吸振器は、上記第２弾性部が上記半径方向に並列に配列された２つの板ばねからなり、上記第２質量部がコの字型であり、上記２つの板ばねの一端が上記コの字型の突出両端の一方の内壁に固定され、他端が上記固定子に接続するための接続部材に固定されているものである。
また、回転子と、上記回転子の外周を囲むように配置された固定子と、上記固定子の外周を覆う筐体と、上記固定子を、上記固定子の外周の面と上記筐体との間に、取り付け位置で支持する弾性部材からなる固定子支持部材と、弾性変形する第１弾性部と上記第１弾性部の一端に取り付けられた第１質量部とを有し、上記第１弾性部の他端が上記固定子に固定されるようにした第１動吸振器とを有し、上記固定子支持部材の取り付け位置が上記固定子の半径方向の振動の腹となり、上記固定子支持部材の取り付け位置から上記固定子の周方向に４５度移動した位置が上記半径方向の振動の節となる第１楕円振動モード、及び上記固定子支持部材の取り付け位置が上記半径方向の振動の節となり、上記固定子支持部材の取り付け位置から周方向に４５度移動した位置が上記半径方向の振動の腹となる第２楕円振動モードが発生する回転電機おいて、
上記第１質量部が上記固定子の周方向に振動するように構成した上記第１動吸振器を、上記第１楕円振動モードの節の位置または上記第２楕円振動モードの節の位置に配設し、上記第１動吸振器は、上記第１弾性部が上記周方向に並列に配列された２つの板ばねからなり、上記第１質量部がコの字型であり、上記２つの板ばねの一端が上記コの字型の第１質量部の突出両端の一方の内壁に固定され、他端が上記固定子に接続するための接続部材に固定されているものである。 A rotating electrical machine according to the present invention includes a rotor, a stator arranged so as to surround the outer periphery of the rotor, a casing covering the outer periphery of the stator, the stator, and an outer periphery of the stator. A stator support member made of an elastic member that is supported at an attachment position, a first elastic part that is elastically deformed, and a first mass part that is attached to one end of the first elastic part between the surface and the housing; A first dynamic vibration absorber having the other end of the first elastic portion fixed to the stator, and the attachment position of the stator support member is the vibration of the stator in the radial direction. The first elliptical vibration mode in which the position moved 45 degrees in the circumferential direction of the stator from the attachment position of the stator support member becomes a node of the radial vibration and the attachment position of the stator support member are It becomes a node of the radial vibration, and the stator support member is removed. Only moved 45 degrees from the position in the circumferential position is kept rotating electric machine in which the second elliptical vibration mode in which the antinodes of the vibration of the radial direction is generated,
The first dynamic vibration absorber configured such that the first mass portion vibrates in the circumferential direction of the stator is disposed at a node position of the first elliptical vibration mode or a node position of the second elliptical vibration mode. was set, the first dynamic vibration absorber includes a first upper having the same thickness as the first elastic portion is made of a plate spring, the same length and two widths of the first elastic part in the first elastic portion of the width No. 1 mass part is sandwiched .
A rotor, a stator disposed so as to surround the outer periphery of the rotor, a casing covering the outer periphery of the stator, the stator, an outer peripheral surface of the stator, and the casing; A stator support member made of an elastic member supported at an attachment position, a first elastic part that is elastically deformed, and a first mass part attached to one end of the first elastic part, and the first A first dynamic vibration absorber whose other end is fixed to the stator, and the attachment position of the stator support member becomes an antinode of vibration in the radial direction of the stator. A first elliptical vibration mode in which the position moved 45 degrees in the circumferential direction of the stator from the attachment position of the support member becomes a node of the radial vibration, and the attachment position of the stator support member is the vibration of the radial direction. From the mounting position of the stator support member. 45 degrees moved position is kept rotating electric machine in which the second elliptical vibration mode in which the antinodes of the vibration of the radial direction is generated,
The first dynamic vibration absorber configured such that the first mass portion vibrates in the circumferential direction of the stator is disposed at a node position of the first elliptical vibration mode or a node position of the second elliptical vibration mode. Set up
When the first dynamic vibration absorber is disposed at the node of the first elliptic vibration mode, the first dynamic vibration absorber is disposed at the antinode position of the first elliptic vibration mode, and the first dynamic vibration absorber is disposed at the node of the second elliptic vibration mode. When disposed, a second dynamic vibration absorber having a second elastic part that is elastically deformed and a second mass part attached to one end of the second elastic part at the antinode of the second elliptical vibration mode. , The second mass part is installed on the stator so as to vibrate in the radial direction of the stator,
The second dynamic vibration absorber includes two leaf springs in which the second elastic portion is arranged in parallel in the radial direction, the second mass portion is a U-shape, and one end of the two leaf springs. Is fixed to one inner wall of both ends of the U-shaped protrusion, and the other end is fixed to a connecting member for connecting to the stator.
A rotor, a stator disposed so as to surround the outer periphery of the rotor, a casing covering the outer periphery of the stator, the stator, an outer peripheral surface of the stator, and the casing; A stator support member made of an elastic member supported at an attachment position, a first elastic part that is elastically deformed, and a first mass part attached to one end of the first elastic part, and the first A first dynamic vibration absorber whose other end is fixed to the stator, and the attachment position of the stator support member becomes an antinode of vibration in the radial direction of the stator. A first elliptical vibration mode in which the position moved 45 degrees in the circumferential direction of the stator from the attachment position of the support member becomes a node of the radial vibration, and the attachment position of the stator support member is the radial vibration. From the mounting position of the stator support member. 45 degrees moved position is kept rotating electric machine in which the second elliptical vibration mode in which the antinodes of the vibration of the radial direction is generated,
The first dynamic vibration absorber configured such that the first mass portion vibrates in the circumferential direction of the stator is disposed at a node position of the first elliptical vibration mode or a node position of the second elliptical vibration mode. was set, the first dynamic vibration absorber, the first elastic portion consists of two leaf springs which are arranged in parallel in the circumferential direction, a shape of the first mass portion is co, the two plates One end of the spring is fixed to one inner wall of the protruding both ends of the U-shaped first mass part, and the other end is fixed to a connecting member for connecting to the stator.

本発明の回転電機は、上記のように構成されているため、振動の腹付近に上記第１動吸振器を設置することが困難であっても、振動の節付近に上記第１動吸振器が固定子の周方向に振動するように設置して、周方向振動を抑振することで、固定子の振動を抑制することができる。 Since the rotating electrical machine of the present invention is configured as described above, even if it is difficult to install the first dynamic vibration absorber near the vibration antinode, the first dynamic vibration absorber is disposed near the vibration node. Is installed so as to vibrate in the circumferential direction of the stator and the circumferential vibration is suppressed, whereby the vibration of the stator can be suppressed.

本発明に係る回転電機の実施の形態１を示す断面図である。It is sectional drawing which shows Embodiment 1 of the rotary electric machine which concerns on this invention. 動吸振器が設置されていない場合の回転電機の断面図である。It is sectional drawing of a rotary electric machine when a dynamic vibration absorber is not installed. 動吸振器が設置されていない場合の回転電機の断面図である。It is sectional drawing of a rotary electric machine when a dynamic vibration absorber is not installed. 本発明に係る回転電機の実施の形態２を示す断面図である。It is sectional drawing which shows Embodiment 2 of the rotary electric machine which concerns on this invention. 本発明に係る回転電機の実施の形態３を示す断面図である。It is sectional drawing which shows Embodiment 3 of the rotary electric machine which concerns on this invention. 本発明に係る回転電機の実施の形態４を示す断面図である。It is sectional drawing which shows Embodiment 4 of the rotary electric machine which concerns on this invention. 本発明に係る回転電機の実施の形態５を示す正面図である。It is a front view which shows Embodiment 5 of the rotary electric machine which concerns on this invention. 本発明に係る回転電機の実施の形態６を示す正面図である。It is a front view which shows Embodiment 6 of the rotary electric machine which concerns on this invention. 振動試験に用いた円筒構造物を示す断面図である。It is sectional drawing which shows the cylindrical structure used for the vibration test. 円筒構造物を用いた振動試験で得た振動応答倍率を示すグラフである。It is a graph which shows the vibration response magnification obtained by the vibration test using a cylindrical structure. 本発明に係る回転電機の実施の形態７に設置された動吸振器を示す斜視図である。It is a perspective view which shows the dynamic vibration damper installed in Embodiment 7 of the rotary electric machine which concerns on this invention. 本発明に係る回転電機の実施の形態８に設置された動吸振器を示す正面図（ａ）及び側面図（ｂ）である。It is the front view (a) and side view (b) which show the dynamic vibration damper installed in Embodiment 8 of the rotary electric machine which concerns on this invention. 本発明に係る回転電機の実施の形態９に設置された動吸振器を示す平面図（ａ）及び正面図（ｂ）である。It is the top view (a) and front view (b) which show the dynamic vibration damper installed in Embodiment 9 of the rotary electric machine which concerns on this invention.

実施の形態１．
本発明に係る回転電機の実施の形態１について、図１〜図３を用いて説明する。図１は、本発明に係る回転電機の実施の形態１を示す断面図、図２及び図３は、動吸振器が設置されていない場合の回転電機の断面図である。図２における破線は固定子２の第１楕円振動モード１０であり、図３における破線は、固定子２の第２楕円振動モード１１である。 Embodiment 1 FIG.
A first embodiment of a rotating electrical machine according to the present invention will be described with reference to FIGS. FIG. 1 is a cross-sectional view showing Embodiment 1 of a rotating electrical machine according to the present invention, and FIGS. 2 and 3 are cross-sectional views of the rotating electrical machine when no dynamic vibration absorber is installed. 2 is the first elliptical vibration mode 10 of the stator 2, and the broken line in FIG. 3 is the second elliptical vibration mode 11 of the stator 2.

本発明の実施の形態１による回転電機において、つるまきばねなどの弾性部材からなる固定子支持部材３は、固定子２の外周面と筐体４との間に、固定子２の周方向に９０度の間隔で３つの取り付け位置８において固定子２の半径方向に弾性変形するように固定されている。固定子２は、回転子１の回転運動に伴って発生した電磁加振力によって生じる２つの楕円振動モード、すなわち、第１楕円振動モードと第２楕円振動モードが発生する。固定子２上の固定子支持部材３の取り付け位置では、固定子２の半径方向振動の腹と節が交互に発生する。これら２つの楕円振動モードの固有振動数はほぼ一致する。 In the rotating electrical machine according to the first embodiment of the present invention, the stator support member 3 made of an elastic member such as a helical spring is disposed between the outer peripheral surface of the stator 2 and the housing 4 in the circumferential direction of the stator 2. The three fixing positions 8 are fixed so as to elastically deform in the radial direction of the stator 2 at intervals of 90 degrees. The stator 2 generates two elliptical vibration modes, that is, a first elliptical vibration mode and a second elliptical vibration mode that are generated by an electromagnetic excitation force generated along with the rotational motion of the rotor 1. At the attachment position of the stator support member 3 on the stator 2, the antinodes and nodes of the radial vibration of the stator 2 are alternately generated. The natural frequencies of these two elliptical vibration modes are almost the same.

図１では、固定子支持部材３は、固定子の左右方向の位置決めのために左右に２つ設け、上下歩行の位置決めのために下側に１つ設ける例を示したが、上下に設けて４つとしてもよい。また、固定子支持部材３は、後述の実施の形態２のように、２つの板ばねからなる固定子支持部材３を平行に配設し、固定子２の接線方向の接点部を支持するように固定子２の外周面と筐体４との間に配置してもよく、第１楕円振動モードと第２楕円振動モードが発生する構造とすればよい。 FIG. 1 shows an example in which two stator support members 3 are provided on the left and right for positioning the stator in the left-right direction and one on the lower side for positioning in the up-and-down direction. It is good also as four. Further, the stator support member 3 is arranged so that the stator support member 3 made of two leaf springs is arranged in parallel as in the second embodiment to be described later, and supports the contact portion in the tangential direction of the stator 2. Further, it may be arranged between the outer peripheral surface of the stator 2 and the housing 4 and may have a structure in which the first elliptical vibration mode and the second elliptical vibration mode are generated.

図２に示したように、第１楕円振動モード１０は半径方向振動が最大値を示す腹１０ａと半径方向振動が０となる節１０ｂをそれぞれ４つずつ有しており、固定子２上の固定子支持部材３の取り付け位置８が腹１０ａとなり、取り付け位置８から４５度移動した位置が節１０ｂとなる。 As shown in FIG. 2, the first elliptical vibration mode 10 has four antinodes 10 a each having a maximum radial vibration and four nodes 10 b each having zero radial vibration. The attachment position 8 of the stator support member 3 becomes the antinode 10a, and the position moved 45 degrees from the attachment position 8 becomes the node 10b.

図３に示したように、第２楕円振動モード１１は、第１楕円振動モード１０と同様に４つの腹１１ａと４つの節１１ｂを有しており、固定子２上の固定子支持部材３の取り付け位置８が節１１ｂとなり、取り付け位置８から４５度移動した位置が腹１１ａとなる。 As shown in FIG. 3, the second elliptical vibration mode 11 has four antinodes 11 a and four nodes 11 b as in the first elliptical vibration mode 10, and the stator support member 3 on the stator 2. The attachment position 8 becomes the node 11b, and the position moved 45 degrees from the attachment position 8 becomes the belly 11a.

固定子２上の固定子支持部材３の取り付け位置で、第１楕円振動モード１０の腹１０ａと第２楕円振動モード１１の節が交互に発生する。 At the attachment position of the stator support member 3 on the stator 2, the nodes 10a of the first elliptical vibration mode 10 and the nodes of the second elliptical vibration mode 11 are alternately generated.

図１に戻り、本実施の形態１では、第１質量部６ａが第１弾性部７ａの一端に固定されてなる第１動吸振器５ａが、固定子２の周方向に振動するように、接続部材１２を用いて図２に示した第１楕円振動モードの節１０ｂ付近に設置されている。固定子２は、電磁加振力の周波数ｆ_０で振動する。第１動吸振器５ａは、固定子２と同じ固有振動数を有するように設計されている。第１動吸振器５ａの第１質量部６ａの質量ｍは、次式（１）で与えられる。
ｍ＝μ・Ｍ・・・・（１）
式中のＭは固定子２の質量であり、μは質量比である。 Returning to FIG. 1, in the first embodiment, the first dynamic vibration absorber 5a in which the first mass portion 6a is fixed to one end of the first elastic portion 7a vibrates in the circumferential direction of the stator 2. The connecting member 12 is used in the vicinity of the node 10b in the first elliptical vibration mode shown in FIG. The stator 2 vibrates at a frequency f ₀ of electromagnetic excitation force. The first dynamic vibration absorber 5 a is designed to have the same natural frequency as that of the stator 2. The mass m of the first mass unit 6a of the first dynamic vibration absorber 5a is given by the following equation (1).
m = μ · M (1)
M in the formula is the mass of the stator 2, and μ is a mass ratio.

また、第１動吸振器５ａのばね定数ｋは次式（２）で与えられる。
ｋ＝４π^２ｆ_０ｍ・・・・（２） The spring constant k of the first dynamic vibration absorber 5a is given by the following equation (2).
k = 4π ² f ₀ m (2)

質量比μを種々の値に変化させた第１動吸振器５ａを用いて、制振効果が得られる条件を実験的または解析的に求める。 Using the first dynamic vibration absorber 5a in which the mass ratio μ is changed to various values, conditions for obtaining the vibration damping effect are obtained experimentally or analytically.

本実施の形態１によれば、第１動吸振器５ａが、固定子２の周方向に振動するように、第１楕円振動モード１０の節１０ｂ付近に設置し、節１０ｂにおける固定子２の周方向振動を抑振することにより径方向振動も抑振される。図１に示したように、第２楕円振動モード１１は抑振できないが、第２楕円振動モード１１の節１１ｂが取り付け位置８となるので、固定子支持部材３の取り付け位置８における第２楕円振動モード１１による振動の影響はない。 According to the first embodiment, the first dynamic vibration absorber 5a is installed near the node 10b of the first elliptical vibration mode 10 so as to vibrate in the circumferential direction of the stator 2, and the stator 2 at the node 10b is arranged. By suppressing the circumferential vibration, the radial vibration is also suppressed. As shown in FIG. 1, the second elliptical vibration mode 11 cannot be suppressed, but the node 11 b of the second elliptical vibration mode 11 is the attachment position 8, so the second ellipse at the attachment position 8 of the stator support member 3. There is no influence of vibration by the vibration mode 11.

図１では、例として第１動吸振器５ａが１箇所のみに設置されているが、第１楕円振動モード１０の全ての節１０ｂ（図２参照）付近に第１動吸振器５ａを設置してもよい。これにより回転電機全体の制振効果が向上し、また、第１動吸振器５ａの１器あたりの重量が軽量化される。 In FIG. 1, as an example, the first dynamic vibration absorber 5 a is installed at only one place, but the first dynamic vibration absorber 5 a is installed near all the nodes 10 b (see FIG. 2) in the first elliptical vibration mode 10. May be. As a result, the vibration damping effect of the entire rotating electrical machine is improved, and the weight of the first dynamic vibration absorber 5a is reduced.

また、図１では、図２で示した第１楕円振動モード１０の節１０ｂ付近に第１動吸振器５ａを設置したが、図３で示した第２楕円振動モード１１の節１１ｂに設けることによって、第２楕円振動モード１１を抑振することができる。 Further, in FIG. 1, the first dynamic vibration absorber 5a is installed near the node 10b of the first elliptical vibration mode 10 shown in FIG. 2, but it is provided at the node 11b of the second elliptical vibration mode 11 shown in FIG. Thus, the second elliptical vibration mode 11 can be suppressed.

実施の形態２．
図４は、本発明に係る回転電機の実施の形態２を示す断面図である。固定子支持部材３は板ばねからなり、２つの板ばねからなる固定子支持部材３は平行に配設され、固定子２の接線方向の接点部を支持するように固定子２の外周面と筐体４との間に配置されている。固定子支持部材３は、固定子支持部材３の面と垂直な方向である面外方向に弾性変形することで、筐体４へ伝達される固定子２の半径方向の振動を抑制する。しかし、固定子支持部材３は、面外方向と垂直な方向である面内方向の剛性が高いため、固定子２の周方向の振動が抑制され難い構造になっている。このため、第２楕円振動モード１１の振動が筐体４に伝達される。そこで、第２楕円振動モード１１の節１１ｂ付近に、第１質量部６ａが固定子２の周方向に振動するように第１動吸振器５ａを設置する。これにより、固定子２上の固定子支持部材３の取り付け位置８における第２楕円振動モード１１を抑振し、周方向の振動を抑制することができる。 Embodiment 2. FIG.
FIG. 4 is a sectional view showing Embodiment 2 of the rotating electrical machine according to the present invention. The stator support member 3 is composed of a leaf spring, and the stator support member 3 composed of two leaf springs is arranged in parallel, and the outer peripheral surface of the stator 2 is supported so as to support a tangential contact portion of the stator 2. It is arranged between the housing 4. The stator support member 3 is elastically deformed in an out-of-plane direction that is a direction perpendicular to the surface of the stator support member 3, thereby suppressing vibration in the radial direction of the stator 2 transmitted to the housing 4. However, since the stator support member 3 has high rigidity in the in-plane direction that is perpendicular to the out-of-plane direction, it has a structure in which the circumferential vibration of the stator 2 is difficult to be suppressed. For this reason, the vibration of the second elliptical vibration mode 11 is transmitted to the housing 4. Therefore, the first dynamic vibration absorber 5a is installed near the node 11b of the second elliptical vibration mode 11 so that the first mass unit 6a vibrates in the circumferential direction of the stator 2. Thereby, the 2nd elliptical vibration mode 11 in the attachment position 8 of the stator support member 3 on the stator 2 can be suppressed, and the vibration of the circumferential direction can be suppressed.

図４では、例として第１動吸振器５ａが１箇所のみに設置されているが、第２楕円振動モード１１の全ての節１１ｂ付近に第１動吸振器５ａを設置してもよい。これにより、回転電機全体の制振効果が向上し、また、第１動吸振器５ａの１器あたり重量が低減される。 In FIG. 4, the first dynamic vibration absorber 5 a is installed only at one place as an example, but the first dynamic vibration absorber 5 a may be installed near all the nodes 11 b in the second elliptical vibration mode 11. Thereby, the damping effect of the whole rotating electrical machine is improved, and the weight per unit of the first dynamic vibration absorber 5a is reduced.

また、第２楕円振動モード１１の節１１ｂの位置に替えて、第１楕円振動モード１０の節１０ｂの位置に第１動吸振器５ａを設置してもよい。これにより、第１楕円振動モード１０を抑振することができる。 Further, instead of the position of the node 11b in the second elliptical vibration mode 11, the first dynamic vibration absorber 5a may be installed at the position of the node 10b in the first elliptical vibration mode 10. Thereby, the first elliptical vibration mode 10 can be suppressed.

実施の形態３．
図５は、本発明に係る回転電機の実施の形態３を示す断面図である。本実施の形態３は上記実施の形態１の変形例であり、第１動吸振器５ａを第１質量部６ａが固定子２の周方向に振動するように第１楕円振動モード１０の節１０ｂ付近に設置し、さらに、第２質量部６ｂが第２弾性部７ｂの一端に固定されてなる第２動吸振器５ｂを、第２質量部６ｂが固定子２の半径方向に振動するように第１楕円振動モード１０の腹１０ａ付近に設置し、第１動吸振器５ａと第２動吸振器５ｂとを組み合わせたものである。この構成によれば、第１動吸振器５ａの第１質量部６ａの質量不足を補うことができ、制振効果を向上させることができる。 Embodiment 3 FIG.
FIG. 5 is a sectional view showing Embodiment 3 of the rotating electrical machine according to the present invention. The third embodiment is a modification of the first embodiment, and the first dynamic vibration absorber 5a is coupled to the node 10b of the first elliptical vibration mode 10 so that the first mass portion 6a vibrates in the circumferential direction of the stator 2. The second dynamic vibration absorber 5b is installed in the vicinity, and the second mass portion 6b is fixed to one end of the second elastic portion 7b, and the second mass portion 6b vibrates in the radial direction of the stator 2. It is installed in the vicinity of the antinode 10a of the first elliptical vibration mode 10, and the first dynamic vibration absorber 5a and the second dynamic vibration absorber 5b are combined. According to this structure, the mass shortage of the 1st mass part 6a of the 1st dynamic vibration absorber 5a can be compensated, and the damping effect can be improved.

また、第１動吸振器５ａと第２動吸振器５ｂとを使用したことによって、１器あたりの重量が低減される。 Further, the use of the first dynamic vibration absorber 5a and the second dynamic vibration absorber 5b reduces the weight per device.

実施の形態４．
図６は、本発明に係る回転電機の実施の形態４を示す断面図である。本実施の形態４は上記実施の形態２の変形例であり、第１動吸振器５ａを第１質量部６ａが固定子２の周方向に振動するように第２楕円振動モード１１の節１１ｂ付近に設置し、さらに、第２質量部６ｂが第２弾性部７ｂに一端に固定されてなる第２動吸振器５ｂを、第２質量部６ｂが固定子２の半径方向に振動するように第２楕円振動モード１１の腹１１ａ付近に設置し、第１動吸振器５ａと第２動吸振器５ｂとを組み合わせたものである。この構成によれば、第１動吸振器５ａの第１質量部６ａの質量不足を補うことができ、制振効果を向上させることができる。 Embodiment 4 FIG.
FIG. 6 is a cross-sectional view showing a fourth embodiment of the rotating electrical machine according to the present invention. The fourth embodiment is a modification of the second embodiment, and the node 11b of the second elliptical vibration mode 11 is arranged such that the first mass absorber 6a vibrates in the circumferential direction of the stator 2 in the first dynamic vibration absorber 5a. The second dynamic vibration absorber 5b is installed near the second elastic portion 7b and the second mass portion 6b is vibrated in the radial direction of the stator 2. It is installed near the antinode 11a of the second elliptical vibration mode 11, and is a combination of the first dynamic vibration absorber 5a and the second dynamic vibration absorber 5b. According to this structure, the mass shortage of the 1st mass part 6a of the 1st dynamic vibration absorber 5a can be compensated, and the damping effect can be improved.

実施の形態５．
図７は、本発明に係る回転電機の実施形態５を示す正面図であり、第１動吸振器５ａの構造例を示す図である。本実施の形態５は、第１動吸振器５ａの第１弾性部７ａとして板ばねを採用したものである。板ばねからなる第１弾性部７ａの一端に角型ブロック状の第１質量部６ａを固定し、板ばねからなる第１弾性部７ａの他端を固定子２に固定するようにしたものであり、固定子２に第１弾性部７ａの他端が固定された第１動吸振器５ａの第１質量部６ａは、矢印で示した並進振動１３ように、固定子２の周方向に振動する。 Embodiment 5 FIG.
FIG. 7 is a front view showing a fifth embodiment of the rotating electrical machine according to the present invention, and is a view showing a structural example of the first dynamic vibration absorber 5a. In the fifth embodiment, a leaf spring is employed as the first elastic portion 7a of the first dynamic vibration absorber 5a. The first mass portion 6a in the form of a square block is fixed to one end of the first elastic portion 7a made of a leaf spring, and the other end of the first elastic portion 7a made of a leaf spring is fixed to the stator 2. Yes, the first mass portion 6a of the first dynamic vibration absorber 5a having the other end of the first elastic portion 7a fixed to the stator 2 vibrates in the circumferential direction of the stator 2 as in the translational vibration 13 indicated by the arrow. To do.

また、第１動吸振器５ａとしての仕様と電磁加振力の周波数ｆ_０との関係は次式（３）で示すことができる。
ｆ_０＝（０．５／π）×（３ＥＩ／ｍ／Ｌ^３）^１／^２・・・・（３）
ここで、Ｌ：第１弾性部（板ばね）７ａの弾性部の長さ、Ｅ：第１弾性部７ａの縦弾性係数、Ｉ：第１弾性部７ａの断面２次モーメントである。 The relationship between the frequency f ₀ of the specification and the electromagnetic excitation force of a first dynamic vibration absorber 5a can be represented by the following formula (3).
_{f 0 = (0.5 / π)} × (3EI / m / L 3) 1/2 ···· (3)
Here, L: length of the elastic part of the first elastic part (plate spring) 7a, E: longitudinal elastic modulus of the first elastic part 7a, and I: secondary moment of section of the first elastic part 7a.

本実施の形態５によれば、第１質量部６ａの幅Ｗ、高さＨと奥行、及び板ばねからなる第１弾性部７ａの断面２次モーメントＩまたは第１弾性部７ａの弾性部の長さＬを調節することによって、固定子２と筐体４との隙間に適合した所望の特性の第１動吸振器５ａが得られる。 According to the fifth embodiment, the width W, the height H and the depth of the first mass portion 6a, and the cross-sectional secondary moment I of the first elastic portion 7a composed of a leaf spring or the elastic portion of the first elastic portion 7a. By adjusting the length L, the first dynamic vibration absorber 5a having desired characteristics adapted to the gap between the stator 2 and the housing 4 can be obtained.

なお、本実施の形態５の第１動吸振器５ａの第１弾性部７ａである板ばねの面を固定子２の外周面と平行になるようにして、図１に示した接続部材１２に接続することで、固定子２の半径方向に振動する第２動吸振器５ｂを構築することができる。 Note that the surface of the leaf spring, which is the first elastic portion 7a of the first dynamic vibration absorber 5a of the fifth embodiment, is parallel to the outer peripheral surface of the stator 2, so that the connection member 12 shown in FIG. By connecting, the second dynamic vibration absorber 5b that vibrates in the radial direction of the stator 2 can be constructed.

実施の形態６．
図８は、本発明に係る回転電機の実施の形態６を示す正面図であり、第１動吸振器５ａの構造例を示す図である。第１動吸振器５ａは、第１弾性部７ａが板ばねからなり、板ばねからなる２つの第１弾性部７ａが左右方向に並列に配設され、２つの第１弾性部７ａの一端が第１質量部６ａを支持するようにしたものである。 Embodiment 6 FIG.
FIG. 8 is a front view showing a sixth embodiment of the rotating electrical machine according to the present invention, and is a view showing a structural example of the first dynamic vibration absorber 5a. In the first dynamic vibration absorber 5a, the first elastic portion 7a is made of a leaf spring, two first elastic portions 7a made of leaf springs are arranged in parallel in the left-right direction, and one end of each of the two first elastic portions 7a is arranged. The first mass part 6a is supported.

本実施の形態６の第１動吸振器５ａの仕様と電磁加振力の周波数ｆ_０の関係は次式（４）で示すことができる。
ｆ_０＝（０．５／π）×（２４ＥＩ／ｍ／Ｌ^３）^１／^２・・・・（４）
ここで、Ｌ：第１弾性部（板ばね）７ａの弾性部の長さ、Ｅ：第１弾性部７ａの縦弾性係数、Ｉ：板ばね７ａの断面２次モーメントである。 Relationship between the frequency f ₀ of the specification and the electromagnetic excitation force of the first dynamic vibration absorber 5a of the sixth embodiment can be represented by the following formula (4).
_{f 0 = (0.5 / π)} × (24EI / m / L 3) 1/2 ···· (4)
Here, L: length of the elastic part of the first elastic part (plate spring) 7a, E: longitudinal elastic modulus of the first elastic part 7a, and I: sectional moment of inertia of the plate spring 7a.

本実施の形態６によれば、第１質量部６ａの幅Ｗ、高さＨと奥行、及び板ばねからなる第１弾性部７ａの断面２次モーメントＩまたは第１弾性部７ａの弾性部の長さＬを調節することによって、固定子２と筐体４との隙間に適合した所望の特性の第１動吸振器５ａが得られる。 According to the sixth embodiment, the width W, height H and depth of the first mass portion 6a, and the cross-sectional secondary moment I of the first elastic portion 7a composed of a leaf spring or the elastic portion of the first elastic portion 7a. By adjusting the length L, the first dynamic vibration absorber 5a having desired characteristics adapted to the gap between the stator 2 and the housing 4 can be obtained.

また、この構成によれば、第１動吸振器５ａの矢印で示した並進振動１３の固有振動数に比べ、第１動吸振器５ａの、例えば、ねじり振動等の他の振動モードの固有振動数を高く設計することによって、並進振動１３の振動モードが他の振動モードの影響を受け難くなるようにすることができる。 Further, according to this configuration, the natural vibration of the first dynamic vibration absorber 5a in another vibration mode such as torsional vibration is compared with the natural frequency of the translational vibration 13 indicated by the arrow of the first dynamic vibration absorber 5a. By designing the number to be high, the vibration mode of the translational vibration 13 can be made less susceptible to other vibration modes.

なお、本実施の形態６の第１動吸振器５ａの第１弾性部７ａの面を固定子２外周面と平行になるようにして、図１に示した接続部材１２に接続することで、固定子２の半径方向に振動する第２動吸振器５ｂを構築することができる。 In addition, by connecting the surface of the first elastic portion 7a of the first dynamic vibration absorber 5a of the sixth embodiment in parallel with the outer peripheral surface of the stator 2, it is connected to the connecting member 12 shown in FIG. The second dynamic vibration absorber 5b that vibrates in the radial direction of the stator 2 can be constructed.

図８の第１動吸振器５ａによる制振効果を確認するため、円筒構造物と第１動吸振器５ａを用いて、楕円振動モードを制振対象として振動試験を実施した。図９は、試験で用いた円筒構造物を示す断面図である。表１に、振動試験に用いた第１動吸振器５ａの諸元を示す。また、表２に、試験条件を示す。図９の円筒構造物１５の点３を半径方向に加振した場合、楕円振動モードは、点１が半径方向における腹に、点２が節になる。 In order to confirm the vibration damping effect by the first dynamic vibration absorber 5a of FIG. 8, a vibration test was performed using the cylindrical structure and the first dynamic vibration absorber 5a with the elliptical vibration mode as a vibration suppression target. FIG. 9 is a cross-sectional view showing a cylindrical structure used in the test. Table 1 shows the specifications of the first dynamic vibration absorber 5a used in the vibration test. Table 2 shows the test conditions. When the point 3 of the cylindrical structure 15 in FIG. 9 is vibrated in the radial direction, the elliptical vibration mode is such that the point 1 is a node in the radial direction and the point 2 is a node.

表２に示したように、第１動吸振器５ａを設置しない場合を条件１とし、円筒構造物１５の半径方向に振動するように第１動吸振器５ａを点１に設置した場合を条件２とし、円筒構造物１５の周方向に振動するように第１動吸振器５ａを点２に設置した場合を条件３とした。表１に示した第１動吸振器５ａの固有振動数は、振動試験で用いた円筒構造物１５の楕円振動モードに合うように設計した。本来なら、第１動吸振器５ａの固有振動数を実機の電磁加振力の周波数に合わせる必要があるが、それができないので、本試験では、第１動吸振器５ａの固有振動数を円筒構造物１５の固有振動数に合わせた。また、本実験では、点３の円筒構造物１５の内周側に加速度計を設けて、各条件における加速度を計測した。 As shown in Table 2, condition 1 is when the first dynamic vibration absorber 5a is not installed, and condition is when the first dynamic vibration absorber 5a is installed at point 1 so as to vibrate in the radial direction of the cylindrical structure 15 2 and condition 3 was set when the first dynamic vibration absorber 5a was installed at point 2 so as to vibrate in the circumferential direction of the cylindrical structure 15. The natural frequency of the first dynamic vibration absorber 5a shown in Table 1 was designed to match the elliptical vibration mode of the cylindrical structure 15 used in the vibration test. Originally, it is necessary to match the natural frequency of the first dynamic vibration absorber 5a with the frequency of the electromagnetic excitation force of the actual machine. However, in this test, the natural frequency of the first dynamic vibration absorber 5a is cylindrical. The natural frequency of the structure 15 was adjusted. In this experiment, an accelerometer was provided on the inner peripheral side of the cylindrical structure 15 at point 3 to measure the acceleration under each condition.

図１０は、振動試験で得られた各条件における加振位置である点３の振動応答倍率（加速度／加振力）をｄＢに変換した値と周波数の関係を示すグラフである。図１０に示したように、円筒構造物１５の固有振動数である２７６Ｈｚにおける振動応答倍率に注目すると、条件１と比較して、条件２では、第１動吸振器５ａの第１質量部６ａが半径方向に振動するように設置することで、振動応答倍率が約８０ｄＢ減少した。一方、第１動吸振器５ａ第１質量部６ａが周方向に振動するように設置した場合、振動応答倍率は約４５ｄＢ減少した。２つの第１動吸振器５ａの振動倍率の低減量に大きな差があるが、節である点２付近に、第１質量部６ａが周方向に運動するように第１動吸振器５ａを設置しても制振効果が得られることが確認された。 FIG. 10 is a graph showing the relationship between the value obtained by converting the vibration response magnification (acceleration / excitation force) at point 3, which is the excitation position under each condition obtained in the vibration test, into dB and the frequency. As shown in FIG. 10, when attention is paid to the vibration response magnification at 276 Hz, which is the natural frequency of the cylindrical structure 15, in the condition 2, the first mass portion 6a of the first dynamic vibration absorber 5a is compared with the condition 1. Was installed so as to vibrate in the radial direction, the vibration response magnification was reduced by about 80 dB. On the other hand, when the first dynamic vibration absorber 5a and the first mass portion 6a are installed so as to vibrate in the circumferential direction, the vibration response magnification is reduced by about 45 dB. Although there is a large difference in the amount of reduction in vibration magnification between the two first dynamic vibration absorbers 5a, the first dynamic vibration absorber 5a is installed near the point 2 that is a node so that the first mass portion 6a moves in the circumferential direction. Even so, it was confirmed that the damping effect was obtained.

実施の形態７．
図１１は、本発明に係る回転電機の実施の形態７を示す斜視図であり、第１動吸振器５ａの構造を示している。図１１に示したように、第１動吸振器５ａは、矢印で示した並進振動１３のように振動するように設計している。第１弾性部７ａは同じ長さと幅の板ばねからなり、２つの第１弾性部７ａの間に第１弾性部７ａの幅と同じ厚さＨを有する第１質量部６ａを挟持した構成となっており、接続部材１２を介して固定子２に設置される。本実施の形態７の第１動吸振器５ａの仕様と電磁加振力の周波数ｆ_０の関係は次式（５）で示すことができる。
ｆ_０＝（０．５／π）×（４８ＥＩ／ｍ／Ｌ^３）^１／^２・・・・（５）
ここで、Ｌ：第１弾性部（板ばね）７ａの弾性部分の長さ、Ｅ：第１弾性部７ａの縦弾性係数、Ｉ：板ばね７ａの断面２次モーメントである。 Embodiment 7 FIG.
FIG. 11 is a perspective view showing a seventh embodiment of the rotating electrical machine according to the present invention, and shows the structure of the first dynamic vibration absorber 5a. As shown in FIG. 11, the first dynamic vibration absorber 5a is designed to vibrate like a translational vibration 13 indicated by an arrow. The 1st elastic part 7a consists of a leaf | plate spring of the same length and width, and comprised the 1st mass part 6a which has the same thickness H as the width | variety of the 1st elastic part 7a between the two 1st elastic parts 7a, and It is installed on the stator 2 via the connecting member 12. Relationship between the frequency f ₀ of the specification and the electromagnetic excitation force of the first dynamic vibration absorber 5a according to the seventh embodiment can be represented by the following formula (5).
_{f 0 = (0.5 / π)} × (48EI / m / L 3) 1/2 ···· (5)
Here, L is the length of the elastic portion of the first elastic portion (plate spring) 7a, E is the longitudinal elastic modulus of the first elastic portion 7a, and I is the cross-sectional secondary moment of the plate spring 7a.

本実施の形態７によれば、第１質量部６ａの幅Ｗ、厚さＨと長さＬ１、及び板ばねからなる第１弾性部７ａの断面２次モーメントＩまたは第１弾性部７ａの弾性部分の長さＬを調節することで第１動吸振器５ａの固有振動数を設計できるため、固定子２と筐体４との隙間に適合する所望の特性の第１動吸振器５ａが得られる。 According to the seventh embodiment, the width W, the thickness H and the length L1 of the first mass portion 6a, and the cross-sectional secondary moment I of the first elastic portion 7a composed of a leaf spring or the elasticity of the first elastic portion 7a. Since the natural frequency of the first dynamic vibration absorber 5a can be designed by adjusting the length L of the portion, the first dynamic vibration absorber 5a having desired characteristics adapted to the gap between the stator 2 and the housing 4 is obtained. It is done.

また、固定子２と筐体４との隙間が狭い場合でも第１質量部６ａ厚さＨを小さくし、長さＬ１と幅Ｗを大きくすることによって対応することができる。 Further, even when the gap between the stator 2 and the housing 4 is narrow, it can be coped with by reducing the thickness H of the first mass part 6a and increasing the length L1 and the width W.

また、第１動吸振器５ａの並進振動１３の固有振動数に比べ、第１動吸振器５ａの、例えば、ねじり等の他の振動モードの固有振動数を高く設計することによって、並進振動１３の振動モードが他の振動モードの影響を受け難くなるようにすることができる。 Further, by designing the natural vibration frequency of the first dynamic vibration absorber 5a to be higher than the natural vibration frequency of the first dynamic vibration absorber 5a, for example, torsional vibration, the translational vibration 13 The vibration mode can be made less susceptible to the influence of other vibration modes.

実施の形態８．
図１２は、本発明に係る回転電機の実施の形態８を示す正面図（ａ）及び側面図（ｂ）である。図１２に示したように、第２動吸振器５ｂは、第２弾性部７ｂが板ばねからなり、２つの第２弾性部７ｂを上下方向に並列に配設し、２つの第２弾性部７ｂの一端が、コの字型をした第２質量部６ｂの両突出部の一方の内壁に固定され、他端が固定子２に接続するための接続部材１２に固定され、第２質量部６ｂが矢印で示した固定子２の半径方向の並進振動１３で振動するように設計している。本実施の形態８による第２動吸振器５ｂの仕様と電磁加振力の周波数ｆ_０の関係は上記式（４）で示すことができる。 Embodiment 8 FIG.
FIG. 12: is the front view (a) and side view (b) which show Embodiment 8 of the rotary electric machine which concerns on this invention. As shown in FIG. 12, in the second dynamic vibration absorber 5b, the second elastic portion 7b is a leaf spring, and the two second elastic portions 7b are arranged in parallel in the vertical direction. One end of 7b is fixed to one inner wall of both projecting portions of the U-shaped second mass portion 6b, and the other end is fixed to the connecting member 12 for connecting to the stator 2, and the second mass portion 6b is designed to vibrate by the translational vibration 13 in the radial direction of the stator 2 indicated by an arrow. Relationship between the frequency f ₀ of the specification and the electromagnetic excitation force of the second dynamic vibration absorber 5b according to the eighth embodiment can be represented by the formula (4).

本実施の形態８によれば、第２動吸振器５ｂの並進振動１３の固有振動数に比べ、例えば、ねじり等の他の振動モードの固有振動数を高く設計することによって、並進振動１３の振動モードが他の振動モードの影響を受け難くなるようにすることができる。 According to the eighth embodiment, by designing the natural frequency of other vibration modes such as torsion, for example, higher than the natural frequency of the translational vibration 13 of the second dynamic vibration absorber 5b, The vibration mode can be made less susceptible to other vibration modes.

また、第２質量部６ｂをコの字型にし、接続部材１２に切り込み部１２ａ形成し、コの字の底部を切り込み部１２ａに配置する等の手段により、第２質量部６ｂの周方向重心が接続部材１２の固定子２への接続部の周方向中心または中心近傍になるようにすることによって、固定子２は、制振対象とする半径方向の振動のみ第２動吸振器５ｂから力を受けることができるようになる。 Further, the center of gravity in the circumferential direction of the second mass portion 6b is formed by means such as making the second mass portion 6b U-shaped, forming the cut portion 12a in the connecting member 12, and arranging the bottom portion of the U-shape in the cut portion 12a. Is set at the center in the circumferential direction of the connecting portion of the connecting member 12 to the stator 2 or in the vicinity of the center, so that the stator 2 can apply force from the second dynamic vibration absorber 5b only in the radial vibration to be controlled. Will be able to receive.

実施の形態９．
図１３は、本発明に係る回転電機の実施の形態８を示す平面図（ａ）及び正面図（ｂ）であり、第１動吸振器５ａが固定子２の周方向に振動するように設計した構造例を示す図である。第１動吸振器５ａは、第１弾性部７ａが板ばねからなり、２つの第１弾性部７ａが左右方向に配設され、２つの第１弾性部７ａの一端がコの字型の第１質量部６ａの両突出部の一方の内壁に固定され、他端が固定子２に接続するための接続部材１２に固定されている。 Embodiment 9 FIG.
FIG. 13 is a plan view (a) and a front view (b) showing an eighth embodiment of the rotating electrical machine according to the present invention, which is designed so that the first dynamic vibration absorber 5a vibrates in the circumferential direction of the stator 2. FIG. In the first dynamic vibration absorber 5a, the first elastic portion 7a is a leaf spring, the two first elastic portions 7a are disposed in the left-right direction, and one end of each of the two first elastic portions 7a is a U-shaped first. The one mass portion 6 a is fixed to one inner wall of both projecting portions, and the other end is fixed to a connecting member 12 for connecting to the stator 2.

本実施の形態９による第１動吸振器５ａの仕様と電磁加振力の周波数ｆ_０の関係は上記式（４）で示すことができる。 Relationship between the frequency f ₀ of the specification and the electromagnetic excitation force of the first dynamic vibration absorber 5a according to the embodiment 9 can be represented by the formula (4).

本実施の形態９によれば、第１動吸振器５ａの並進振動１３の方向の固有振動数に比べ、例えば、ねじれ方向等の他の振動モードの固有振動数を高く設計することにより、並進振動１３の振動モードが他の振動モードの影響を受け難くなるようにすることができる。 According to the ninth embodiment, the natural frequency in the other vibration mode such as the torsional direction is designed to be higher than the natural frequency in the direction of the translational vibration 13 of the first dynamic vibration absorber 5a. The vibration mode of the vibration 13 can be made difficult to be influenced by other vibration modes.

なお、本発明は、その発明の範囲内において、各実施の形態を自由に組み合わせたり、各実施の形態を適宜、変形、省略することが可能である。 It should be noted that the present invention can be freely combined with each other within the scope of the invention, and each embodiment can be appropriately modified or omitted.

本発明に係る回転電機は、タービン発電機等の回転電機として有効に利用することができる。 The rotating electrical machine according to the present invention can be effectively used as a rotating electrical machine such as a turbine generator.

１回転子、２固定子、３固定子支持部材、４筐体、５ａ第１動吸振器、
５ｂ第２動吸振器、６ａ第１質量部、６ｂ第２質量部、７ａ第１弾性部、
７ｂ第２弾性部、８取り付け位置、１０第１楕円振動モード、
１０ａ，１１ａ腹、１０ｂ，１１ｂ節、１１第２楕円振動モード、
１２接続部材、１３並進振動、１５円筒構造物。 1 rotor, 2 stator, 3 stator support member, 4 housing, 5a first dynamic vibration absorber,
5b 2nd dynamic vibration absorber, 6a 1st mass part, 6b 2nd mass part, 7a 1st elastic part,
7b 2nd elastic part, 8 attachment position, 10 1st elliptical vibration mode,
10a, 11a belly, 10b, 11b node, 11 second elliptical vibration mode,
12 connection member, 13 translational vibration, 15 cylindrical structure.

Claims

回転子と、上記回転子の外周を囲むように配置された固定子と、上記固定子の外周を覆う筐体と、上記固定子を、上記固定子の外周の面と上記筐体との間に、取り付け位置で支持する弾性部材からなる固定子支持部材と、弾性変形する第１弾性部と上記第１弾性部の一端に取り付けられた第１質量部とを有し、上記第１弾性部の他端が上記固定子に固定されるようにした第１動吸振器とを有し、上記固定子支持部材の取り付け位置が上記固定子の半径方向の振動の腹となり、上記固定子支持部材の取り付け位置から上記固定子の周方向に４５度移動した位置が上記半径方向の振動の節となる第１楕円振動モード、及び上記固定子支持部材の取り付け位置が上記半径方向の振動の節となり、上記固定子支持部材の取り付け位置から周方向に４５度移動した位置が上記半径方向の振動の腹となる第２楕円振動モードが発生する回転電機おいて、
上記第１質量部が上記固定子の周方向に振動するように構成した上記第１動吸振器を、上記第１楕円振動モードの節の位置または上記第２楕円振動モードの節の位置に配設し、上記第１動吸振器は、上記第１弾性部が板ばねからなり、同じ長さと幅の２つの上記第１弾性部で上記第１弾性部の幅と同じ厚さを有する上第１記質量部を挟持してなることを特徴とする回転電機。 A rotor, a stator arranged so as to surround the outer periphery of the rotor, a housing covering the outer periphery of the stator, and the stator between the outer peripheral surface of the stator and the housing A stator support member made of an elastic member that is supported at the attachment position, a first elastic part that is elastically deformed, and a first mass part that is attached to one end of the first elastic part, and the first elastic part The other end of the stator is fixed to the stator, and the attachment position of the stator support member becomes the antinode of the radial vibration of the stator, and the stator support member The first elliptical vibration mode in which the position moved 45 degrees in the circumferential direction of the stator from the mounting position is the radial vibration node, and the mounting position of the stator support member is the radial vibration node. 45 in the circumferential direction from the mounting position of the stator support member. Moved position is kept rotating electric machine in which the second elliptical vibration mode in which the antinodes of the vibration of the radial direction is generated,
The first dynamic vibration absorber configured such that the first mass portion vibrates in the circumferential direction of the stator is disposed at a node position of the first elliptical vibration mode or a node position of the second elliptical vibration mode. was set, the first dynamic vibration absorber includes a first upper having the same thickness as the first elastic portion is made of a plate spring, the same length and two widths of the first elastic part in the first elastic portion of the width A rotating electric machine characterized by sandwiching one mass part .

回転子と、上記回転子の外周を囲むように配置された固定子と、上記固定子の外周を覆う筐体と、上記固定子を、上記固定子の外周の面と上記筐体との間に、取り付け位置で支持する弾性部材からなる固定子支持部材と、弾性変形する第１弾性部と上記第１弾性部の一端に取り付けられた第１質量部とを有し、上記第１弾性部の他端が上記固定子に固定されるようにした第１動吸振器とを有し、上記固定子支持部材の取り付け位置が上記固定子の半径方向の振動の腹となり、上記固定子支持部材の取り付け位置から上記固定子の周方向に４５度移動した位置が上記半径方向の振動の節となる第１楕円振動モード、及び上記固定子支持部材の取り付け位置が上記半径方向の振動の節となり、上記固定子支持部材の取り付け位置から周方向に４５度移動した位置が上記半径方向の振動の腹となる第２楕円振動モードが発生する回転電機おいて、
上記第１質量部が上記固定子の周方向に振動するように構成した上記第１動吸振器を、上記第１楕円振動モードの節の位置または上記第２楕円振動モードの節の位置に配設し、
上記第１動吸振器を上記第１楕円振動モードの節に配設した場合には上記第１楕円振動モードの腹の位置に、上記第１動吸振器を上記第２楕円振動モードの節に配設した場合には上記第２楕円振動モードの腹の位置に、弾性変形する第２弾性部と上記第２弾性部の一端に取り付けられた第２質量部とを有する第２動吸振器を、上記第２質量部が上記固定子の半径方向に振動するように上記固定子に設置し、
上記第２動吸振器は、上記第２弾性部が上記半径方向に並列に配列された２つの板ばねからなり、上記第２質量部がコの字型であり、上記２つの板ばねの一端が上記コの字型の突出両端の一方の内壁に固定され、他端が上記固定子に接続するための接続部材に固定されていることを特徴とする回転電機。 A rotor, a stator arranged so as to surround the outer periphery of the rotor, a housing covering the outer periphery of the stator, and the stator between the outer peripheral surface of the stator and the housing A stator support member made of an elastic member that is supported at the attachment position, a first elastic part that is elastically deformed, and a first mass part that is attached to one end of the first elastic part, and the first elastic part The other end of the stator is fixed to the stator, and the attachment position of the stator support member becomes the antinode of the radial vibration of the stator, and the stator support member The first elliptical vibration mode in which the position moved 45 degrees in the circumferential direction of the stator from the mounting position is the radial vibration node, and the mounting position of the stator support member is the radial vibration node. 45 in the circumferential direction from the mounting position of the stator support member. Moved position is kept rotating electric machine in which the second elliptical vibration mode in which the antinodes of the vibration of the radial direction is generated,
The first dynamic vibration absorber configured such that the first mass portion vibrates in the circumferential direction of the stator is disposed at a node position of the first elliptical vibration mode or a node position of the second elliptical vibration mode. Set up
When the first dynamic vibration absorber is disposed at the node of the first elliptic vibration mode, the first dynamic vibration absorber is disposed at the antinode position of the first elliptic vibration mode, and the first dynamic vibration absorber is disposed at the node of the second elliptic vibration mode. When disposed, a second dynamic vibration absorber having a second elastic part that is elastically deformed and a second mass part attached to one end of the second elastic part at the antinode of the second elliptical vibration mode. , The second mass part is installed on the stator so as to vibrate in the radial direction of the stator,
The second dynamic vibration absorber includes two leaf springs in which the second elastic portion is arranged in parallel in the radial direction, the second mass portion is a U-shape, and one end of the two leaf springs. Is fixed to one inner wall at both ends of the U-shaped projecting end, and the other end is fixed to a connecting member for connecting to the stator.

上記第２質量部の周方向重心が、上記接続部材の上記固定子への接続部の周方向中心に位置するようにしたことを特徴とする請求項２に記載の回転電機。 3. The rotating electrical machine according to claim 2 , wherein the center of gravity of the second mass portion in the circumferential direction is positioned at the center in the circumferential direction of the connection portion of the connection member to the stator.

回転子と、上記回転子の外周を囲むように配置された固定子と、上記固定子の外周を覆う筐体と、上記固定子を、上記固定子の外周の面と上記筐体との間に、取り付け位置で支持する弾性部材からなる固定子支持部材と、弾性変形する第１弾性部と上記第１弾性部の一端に取り付けられた第１質量部とを有し、上記第１弾性部の他端が上記固定子に固定されるようにした第１動吸振器とを有し、上記固定子支持部材の取り付け位置が上記固定子の半径方向の振動の腹となり、上記固定子支持部材の取り付け位置から上記固定子の周方向に４５度移動した位置が上記半径方向の振動の節となる第１楕円振動モード、及び上記固定子支持部材の取り付け位置が上記半径方向の振動の節となり、上記固定子支持部材の取り付け位置から周方向に４５度移動した位置が上記半径方向の振動の腹となる第２楕円振動モードが発生する回転電機おいて、
上記第１質量部が上記固定子の周方向に振動するように構成した上記第１動吸振器を、上記第１楕円振動モードの節の位置または上記第２楕円振動モードの節の位置に配設し、上記第１動吸振器は、上記第１弾性部が上記周方向に並列に配列された２つの板ばねからなり、上記第１質量部がコの字型であり、上記２つの板ばねの一端が上記コの字型の第１質量部の突出両端の一方の内壁に固定され、他端が上記固定子に接続するための接続部材に固定されていることを特徴とする回転電機。 A rotor, a stator arranged so as to surround the outer periphery of the rotor, a housing covering the outer periphery of the stator, and the stator between the outer peripheral surface of the stator and the housing A stator support member made of an elastic member that is supported at the attachment position, a first elastic part that is elastically deformed, and a first mass part that is attached to one end of the first elastic part, and the first elastic part The other end of the stator is fixed to the stator, and the attachment position of the stator support member becomes the antinode of the radial vibration of the stator, and the stator support member The first elliptical vibration mode in which the position moved 45 degrees in the circumferential direction of the stator from the mounting position is the radial vibration node, and the mounting position of the stator support member is the radial vibration node. 45 in the circumferential direction from the mounting position of the stator support member. Moved position is kept rotating electric machine in which the second elliptical vibration mode in which the antinodes of the vibration of the radial direction is generated,
The first dynamic vibration absorber configured such that the first mass portion vibrates in the circumferential direction of the stator is disposed at a node position of the first elliptical vibration mode or a node position of the second elliptical vibration mode. was set, the first dynamic vibration absorber consists of two leaf springs which the first elastic portion are arranged in parallel with the circumferential direction, a shape of the first mass portion is co, the two one end of the leaf spring is fixed to one inner wall of the projecting ends of the first mass portions of shaped the co and the other end you characterized in that it is fixed to the connecting member for connection to the stator rotating electrical machinery.