WO2019106761A1 - Centrifugal fan and dynamo-electric machine - Google Patents

Centrifugal fan and dynamo-electric machine Download PDF

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Publication number
WO2019106761A1
WO2019106761A1 PCT/JP2017/042842 JP2017042842W WO2019106761A1 WO 2019106761 A1 WO2019106761 A1 WO 2019106761A1 JP 2017042842 W JP2017042842 W JP 2017042842W WO 2019106761 A1 WO2019106761 A1 WO 2019106761A1
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Prior art keywords
centrifugal fan
blade
blades
front edge
main plate
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PCT/JP2017/042842
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French (fr)
Japanese (ja)
Inventor
惠介 武石
眞一郎 南
拓也 石田
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三菱電機株式会社
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Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to JP2019556463A priority Critical patent/JP7062684B2/en
Priority to PCT/JP2017/042842 priority patent/WO2019106761A1/en
Publication of WO2019106761A1 publication Critical patent/WO2019106761A1/en

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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
    • F04D—NON-POSITIVE-DISPLACEMENT PUMPS
    • F04D29/00—Details, component parts, or accessories
    • F04D29/26—Rotors specially for elastic fluids
    • F04D29/28—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps
    • F04D29/30—Vanes
    • H—ELECTRICITY
    • H02—GENERATION; CONVERSION OR DISTRIBUTION OF ELECTRIC POWER
    • H02K—DYNAMO-ELECTRIC MACHINES
    • H02K9/00—Arrangements for cooling or ventilating
    • H02K9/02—Arrangements for cooling or ventilating by ambient air flowing through the machine
    • H02K9/04—Arrangements for cooling or ventilating by ambient air flowing through the machine having means for generating a flow of cooling medium
    • H02K9/06—Arrangements for cooling or ventilating by ambient air flowing through the machine having means for generating a flow of cooling medium with fans or impellers driven by the machine shaft

Definitions

  • the present invention relates to a centrifugal fan for improving cooling performance, and a rotary electric machine equipped with the centrifugal fan.
  • Centrifugal fans are used to transport gases such as air or liquids such as refrigerants.
  • the centrifugal fan of Patent Document 1 includes a plurality of blades arranged in the circumferential direction, and a disk-shaped or bowl-shaped hub provided at one end in the axial direction of the blades.
  • centrifugal fan with an annular shroud at the end of the plurality of circumferentially arranged vanes opposite to the hub.
  • centrifugal fan high efficiency and low noise have been achieved by suppressing separation occurring at the front edge of each blade (see, for example, Patent Documents 1 to 3).
  • the centrifugal fan described in Patent Document 3 reduces the noise source by having a structure in which the suction portion of the blade leading edge is rounded.
  • the centrifugal fan of Patent Document 3 has a problem that it is small as an effect of noise reduction.
  • the present invention is made to solve the above-mentioned problems, and it is an object of the present invention to provide a centrifugal fan and a rotary electric machine capable of achieving both noise reduction and improvement of cooling performance.
  • a centrifugal fan is a centrifugal fan including a main plate, a plurality of wings provided on the main plate, and a plurality of wings provided on each of the plurality of wings.
  • the end face on the rotary shaft side of the centrifugal fan is defined as a front edge, and at the front edge of the blades, the shape of the blade at the front edge forms an angle with the circumferential direction of the centrifugal fan.
  • the blades are formed so that the inlet installation angle changes according to the height of the centrifugal fan in the rotational axis direction, and between the main plate side and the suction side of the blades , And is formed to have an extreme value at which the inlet installation angle is maximum.
  • the noise source at the leading edge of the blade is reduced, and the flow rate flowing in the rotational axis direction is increased to improve the cooling performance.
  • FIG. 1 is an overall view showing a centrifugal fan according to Embodiment 1 of the present invention. It is sectional drawing which looked at the centrifugal fan in FIG. 1 from the orthogonal
  • FIG. 1 is a configuration diagram of a centrifugal fan 1 according to Embodiment 1 of the present invention.
  • the centrifugal fan 1 includes a main plate 3 and a plurality of blades 2.
  • the main plate 3 has a plate-like shape, and the rotation shaft hole 5 is provided at the center thereof.
  • the rotation shaft hole 5 of the main plate 3 may have a shape in which the center is expanded like a bowl.
  • the main plate 3 may have a shape provided with a hole for passing a shaft for rotation to the center.
  • the main plate 3 may have a shape provided with a projection such as a rib from the strength surface.
  • a plurality of wings 4 are radially provided at intervals in the circumferential direction of the main plate 3.
  • a notch is provided between adjacent wings 4.
  • the wing 4 is provided on the wing 4 in the rotation axis direction. Arrows in FIG. 1 indicate directions in which the centrifugal fan rotates about the rotation shaft hole 4.
  • the rotary shaft side is the front edge 2a of the blade
  • the outer edge of the blade 2 is the rear edge 2b of the blade.
  • the front edge 2 a of the blade is provided to be inclined in the rotational direction of the centrifugal fan 1. That is, as the leading edge 2 a moves away from the main plate 3 and the wing 4, the blades 2 will gradually rotate in the rotational direction of the centrifugal fan 1.
  • the angle between the blade leading edge 2a and the circumferential direction of the circle passing through the leading edge about the rotation axis there is no flow collision at the blade leading edge and noise generated by the blade is reduced.
  • the negative pressure generated on the negative pressure surface of the blade 2 can be further reduced.
  • the flow rate flowing in the rotational axis direction can be increased. As a result, the flow rate can be increased by the structure of the centrifugal fan shown in FIG.
  • FIG. 2 is a cross-sectional view of the centrifugal fan in FIG. 1 as viewed from the vertical direction of the rotation axis.
  • FIG. 3 is a view for explaining the installation angle of the centrifugal fan.
  • FIG. 4 is a graph showing the correspondence between the height in the rotational axis direction of the blades of the centrifugal fan and the inlet installation angle.
  • FIG. 5 is a view for explaining the rotation angle of the leading edge position on the suction side with respect to the leading edge position on the main plate side of the centrifugal fan.
  • the blade height in the description refers to the height of the blade in a cross section perpendicular to the rotational axis direction of the centrifugal fan 1.
  • the upper side of the drawing is the suction side of the centrifugal fan 1
  • the lower side of the drawing is the main plate 3 side.
  • Cross sections at positions of blade heights A, B and C from the suction side of the centrifugal fan in the height direction of the blades 2 are taken as a cross section A, a cross section B and a cross section C, respectively.
  • the dotted line in FIG. 3 represents the circumference of the main plate 3 at the root portion of the notch.
  • the shape of the blade 2 in the cross section at each height of A, B and C makes an angle with the circumferential direction as an inlet installation angle ⁇ A , an inlet installation angle ⁇ B , and an inlet Set as the installation angle ⁇ C.
  • FIG. 4 shows the correspondence between the height of the blade 2 in the rotational axis direction and the inlet installation angle.
  • the vertical axis represents the height of the blade 2 in the rotational axis direction as a ratio to the maximum blade height.
  • the horizontal axis represents the inlet installation angle ⁇ [°].
  • the solid line shows the correspondence in the present invention, and the broken line shows the correspondence in the prior art.
  • the relationship of ⁇ A ⁇ B and ⁇ C ⁇ B is established among the inlet installation angles ⁇ A , ⁇ B and ⁇ C.
  • the inlet installation angle ⁇ A and the inlet installation angle ⁇ B are preferably set in the range of ⁇ 10 ⁇ ⁇ A ⁇ 30, 20 ⁇ ⁇ B ⁇ 70, and ⁇ C is an arbitrary angle less than ⁇ B. Good.
  • the flow rate flowing in the circumferential direction with respect to the blades 2 can be reduced by reducing the inlet installation angle on the main plate 3 side.
  • the collision between the flow passing from the suction side of the centrifugal fan 1 toward the main plate 3 and the flow in the circumferential direction decreases, and the flow rate in the rotational axis direction can be increased.
  • the present blade 2 has such a leading edge shape, and the flow rate is increased by about 10% as compared with the blade 2 of the prior art, and the noise value is approximately 0. 0 in overall value. It could be reduced by 3 dB.
  • the inlet installation angles ⁇ A , ⁇ B , and ⁇ C are the same for all the blades.
  • the rotational noise generated by the centrifugal fan 1 without reducing the air volume of the centrifugal fan 1 by changing the inlet installation angle according to the height direction of the blades 2 Can be modulated to reduce noise. That is, the centrifugal fan according to the present invention can realize the effect of increasing the flow rate in the direction of the rotation axis after noise reduction.
  • the inlet installation angle of the blades 2 is designed to increase at least once from the main plate 3 side to the suction side in the height direction of the blades 2 and decrease at least once. That is, the inlet installation angle has one extreme value at a certain height B in the height direction of the blade 2.
  • the inlet installation angle of the front edge of the blade 2 increases once from C position to B position on the main plate side and decreases once from B position to A position on the suction side. It has one extremum.
  • the ratio to the maximum blade height is 0.4 to 0.5.
  • wing 2 may have several extreme value so that it may become large and it may become small after that several times.
  • FIG. 5 is a diagram for explaining the rotation angle of the leading edge position on the suction side of the centrifugal fan.
  • the radius from the rotation center axis of the front edge of the blade 2 is approximately equal, and the rotation angle ⁇ [°] is the angle between the front edge on the main plate 3 and the front edge on the suction side, where O is the rotation center of the centrifugal fan 1 Set
  • the front edge on the suction side may be rotated about the front edge on the main plate 3 side in the rotational direction.
  • FIG. 6 is a graph showing the relationship between the flow rate of the centrifugal fan 1 and the rotational angle ⁇ ⁇ of the blades.
  • the vertical axis represents increase or decrease [%] of suction flow rate
  • the horizontal axis represents blade rotation angle ⁇ [°].
  • the noise generated from the centrifugal fan 1 can be reduced and the suction flow rate can be increased.
  • the front edge of the blade 2 is rounded in an arc shape. May be
  • FIG. 7 is a view showing a blade shape of the centrifugal fan 1.
  • the front edge position of the blade 2 is D
  • the rear edge position of the blade 2 is F.
  • an arbitrary position between the front edge position D and the rear edge position F of the blade 2 is E.
  • the shape of the blade 4 from the leading edge position D of the blade 2 to the arbitrary position E differs depending on the height direction of the blade
  • the shape of the blade 4 from the arbitrary position E of the blade to the trailing edge position F is It may be designed to be substantially the same in all the height directions of the blades.
  • a vehicular AC generator 100 as one embodiment to which the present invention is applied is shown in FIG.
  • the automotive alternator 100 includes the centrifugal fan 83, the casing 4, the pair of bearings 5, the shaft 6, the pulley 7, the rotor 8, the stator 9, and the slip ring 10 according to the first embodiment.
  • the casing 4 includes a substantially wedge-shaped front housing 31 made of aluminum and a rear housing 30.
  • the casing 4 includes a shaft 6 rotatably supported via a pair of bearings 5.
  • a pulley 7 is fixed to an end of the shaft 6 extending to the front side of the casing 4.
  • a rotor 8 that rotates integrally with the shaft 6 is disposed.
  • the stator 9 is disposed opposite to the outer periphery of the rotor 8, and the stator 9 is fixed to the casing 4.
  • a pair of slip rings 10 for supplying an electric current to the rotor 8 is fixed to the shaft 6 extended to the rear side of the casing 4.
  • a voltage regulator 12 for adjusting the magnitude of the AC voltage generated in the stator 9 adjacent to the brush 11, a rectifier 13 for rectifying the AC voltage generated in the stator 9 into a DC voltage, a heat sink 18;
  • a connector 20 is provided to input and output signals between the voltage regulator 12 and an external device (not shown).
  • a protective cover 27 is provided to cover the brush holder 17 and the rectifying device 13.
  • the rotor 8 is formed of a field winding 81 and a field iron core 82, and is provided with an air passage for cooling the field winding.
  • Each of the field cores 82 has six or eight claws, and is provided so as to cover the field winding 81.
  • the field winding 81 is a Lundell-type rotor, and is wound cylindrically and concentrically with an insulated copper wire, and an excitation current flows to generate a magnetic flux.
  • a magnetic pole is formed by the magnetic flux generated by the field winding 81.
  • the centrifugal fan 83 is attached to both end surfaces of the rotor 8 by welding or the like.
  • the present invention is not limited to this.
  • the present invention can also be used by attaching to, for example, a rotor of a rotating electrical machine such as an on-vehicle alternating current generator, a motor, or an on-vehicle drive device.
  • the centrifugal fan according to the first embodiment includes a main plate, a plurality of wings provided on the main plate, and a wing provided on the wing, and the inlet installation angle of the leading edge of the wing is set to a height in the rotational axis direction of the centrifugal fan Change according to the Specifically, in the centrifugal fan according to the first embodiment, the inlet installation angle of the leading edge of the blade increases and then decreases as it goes from the main plate side to the suction side, and then the inlet installation angle is at least one pole. It has a blade with a value.
  • the flow rate in the rotational axis direction of the centrifugal fan can be increased. Therefore, after reducing the noise generated from the centrifugal fan, the suction flow rate can be increased, and both noise reduction and improvement of the cooling performance can be achieved.
  • Each of the plurality of vanes may have vane heights having extrema of the inlet installation angle set to different heights. Thereby, it is possible to increase the flow rate in the rotational axis direction of the centrifugal fan differently for each blade. Furthermore, the shape of the blades differs depending on the direction of rotation. For this reason, without reducing the air volume of the fan, noise related to the rotational speed of the centrifugal fan can be dispersed and modulated to the frequency around it to reduce noise.
  • the leading edge of the blade is inclined in the direction of rotation of the centrifugal fan.
  • Such a configuration of the blades causes the leading edge of the blades to rotate gradually and quickly in the direction of rotation of the centrifugal fan as it moves away from the main plate and the blades.
  • noise related to the rotational speed of the centrifugal fan can be dispersed and modulated to frequencies around it to reduce noise.
  • the blades can be designed such that the curve from the leading edge position to the arbitrary position is different for each blade, and the curve from the arbitrary position to the trailing edge position is equal in at least two blades.
  • noise sources present at the leading edge of the blade can be effectively reduced by making the shape of the leading edge of the blade different in the height direction of the blade.
  • the noise generated from the centrifugal fan can be reduced.
  • by equalizing the shape of the trailing edge of all the vanes in the height direction of the vanes it is possible to suppress a decrease in suction flow rate.
  • a blade For the leading edge on the main plate side, a blade can be designed in which the rotational direction ⁇ of the leading edge on the suction side is 0 ⁇ 0 ⁇ 10. Thereby, the suction flow rate of the centrifugal fan can be increased, and the cooling capacity can be improved. Therefore, both noise reduction and improvement of the cooling performance can be achieved.
  • the centrifugal fan according to the present invention can be applied to a rotating electrical machine. Such an application can increase the flow rate flowing in the direction of the rotation shaft of the rotating electrical machine. As a result, it is possible to realize a rotating electrical machine that achieves both noise reduction and improvement in cooling performance.
  • the centrifugal fan according to the present invention can also be configured to include an annular shroud so as to be positioned upstream and face the main plate of the blade.
  • FIG. 1 The structure of the blade
  • an arbitrary point G is set at the front edge of the blade 2, and an arbitrary point H is set at the suction side of the blade 2.
  • the blade 2 according to the second embodiment has a structure in which the blade 2 is inclined to be bent in the rotational direction by a straight line passing through the point G and the point H.
  • the flow rate in the rotational axis direction of the centrifugal fan can also be increased. As a result, while achieving both noise reduction and improvement in cooling performance, it is possible to realize performance improvement in noise reduction as compared to the first embodiment.

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  • Engineering & Computer Science (AREA)
  • Power Engineering (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Motor Or Generator Cooling System (AREA)

Abstract

A centrifugal fan comprising a main plate, a plurality of vanes, and a plurality of blades, wherein when the angle forming the circumferential direction of the centrifugal fan is defined as the inlet placement angle, the shape of each blade at the front edge part is formed so that the inlet placement angle of the blade varies in accordance with the height in the rotation axis direction of the centrifugal fan, and is formed so that the inlet placement angle has a maximum extreme value between the main plate side and the intake side of the blade.

Description

遠心ファンおよび回転電機Centrifugal fan and rotating electric machine
　本発明は、冷却性能の向上を図る遠心ファン、および遠心ファンを備えた回転電機に関する。 The present invention relates to a centrifugal fan for improving cooling performance, and a rotary electric machine equipped with the centrifugal fan.
　遠心ファンは、空気をはじめとする気体、あるいは冷媒のような液体を輸送する目的で使用されている。例えば、特許文献１の遠心ファンでは、円周方向に複数配置される羽根と、羽根の軸方向の一端に設けられた円盤状あるいはお椀状のハブとを備えている。 Centrifugal fans are used to transport gases such as air or liquids such as refrigerants. For example, the centrifugal fan of Patent Document 1 includes a plurality of blades arranged in the circumferential direction, and a disk-shaped or bowl-shaped hub provided at one end in the axial direction of the blades.
　また、円周方向に複数配置される羽根のハブとは反対の端に、円環状のシュラウドを備えている遠心ファンも存在する。従来、このような遠心ファンにおいては、各羽根の前縁で発生する剥離を抑制することで、高効率化と低騒音化を図っている（例えば、特許文献１～３参照）。 There is also a centrifugal fan with an annular shroud at the end of the plurality of circumferentially arranged vanes opposite to the hub. Conventionally, in such a centrifugal fan, high efficiency and low noise have been achieved by suppressing separation occurring at the front edge of each blade (see, for example, Patent Documents 1 to 3).
特開２０１４－２０２１９８号公報JP, 2014-202198, A 特開平２－７０９９７号公報Japanese Patent Application Laid-Open No. 2-7099 特開平９－２０１００９号公報Japanese Patent Application Laid-Open No. 9-201009
　しかしながら、従来技術には以下のような問題がある。
　特許文献１および特許文献２に記載された遠心ファンの構造は、羽根の前縁部で発生する騒音が低減されるため、低騒音効果はある。その一方でこれらの遠心ファンは、同時に流量が低下してしまうという問題があった。 However, the prior art has the following problems.
The structure of the centrifugal fan described in Patent Document 1 and Patent Document 2 has a low noise effect because the noise generated at the front edge of the blade is reduced. On the other hand, these centrifugal fans have a problem that the flow rate is simultaneously reduced.
　また、特許文献３に記載された遠心ファンは、羽根前縁の吸込み部分を丸くする構造を有することで騒音源を小さくしている。しかしながら、特許文献３の遠心ファンは、低騒音化の効果としては小さいという問題があった。 Moreover, the centrifugal fan described in Patent Document 3 reduces the noise source by having a structure in which the suction portion of the blade leading edge is rounded. However, the centrifugal fan of Patent Document 3 has a problem that it is small as an effect of noise reduction.
　さらに、特許文献１から３のいずれの遠心ファンも、回転軸方向の流量を増加させる効果はないという問題があった。 Furthermore, there is a problem that none of the centrifugal fans of Patent Documents 1 to 3 have the effect of increasing the flow rate in the rotational axis direction.
　本発明は、上記のような問題を解決するためになされるもので、低騒音化と冷却性能の向上の両立を図ることのできる遠心ファンおよび回転電機を提供することを目的とする。 The present invention is made to solve the above-mentioned problems, and it is an object of the present invention to provide a centrifugal fan and a rotary electric machine capable of achieving both noise reduction and improvement of cooling performance.
　上記の課題を解決するために、本発明に係る遠心ファンは、主板と、主板に設けられた複数の翼と、複数の翼のそれぞれに設けられた複数の羽根とを備える遠心ファンであって、複数の羽根のそれぞれにおいて、遠心ファンの回転軸側の端面を前縁部と規定し、羽根の前縁部において、前縁部における羽根の形状が、遠心ファンの円周方向と成す角度を入口設置角度と規定した際に、羽根は、遠心ファンの回転軸方向の高さに応じて入口設置角度が変化するように形成されており、かつ、羽根の主板側と吸込み側との間において、入口設置角度が最大となる極値を有するように形成されているものである。 In order to solve the above problems, a centrifugal fan according to the present invention is a centrifugal fan including a main plate, a plurality of wings provided on the main plate, and a plurality of wings provided on each of the plurality of wings. In each of the plurality of blades, the end face on the rotary shaft side of the centrifugal fan is defined as a front edge, and at the front edge of the blades, the shape of the blade at the front edge forms an angle with the circumferential direction of the centrifugal fan When the inlet installation angle is defined, the blades are formed so that the inlet installation angle changes according to the height of the centrifugal fan in the rotational axis direction, and between the main plate side and the suction side of the blades , And is formed to have an extreme value at which the inlet installation angle is maximum.
　本発明に係る遠心ファンによれば、羽根前縁部の騒音源を小さくするとともに、回転軸方向へ流れる流量を増加させ、冷却性能を高める構造を備えている。この結果、低騒音化と冷却性能の向上の両立を図ることのできる遠心ファンを提供することができる。 According to the centrifugal fan according to the present invention, the noise source at the leading edge of the blade is reduced, and the flow rate flowing in the rotational axis direction is increased to improve the cooling performance. As a result, it is possible to provide a centrifugal fan capable of achieving both noise reduction and improvement of cooling performance.
本発明の実施の形態１に係る遠心ファンを示す全体図である。1 is an overall view showing a centrifugal fan according to Embodiment 1 of the present invention. 図１における遠心ファンを回転軸の垂直方向から見た断面図である。It is sectional drawing which looked at the centrifugal fan in FIG. 1 from the orthogonal | vertical direction of the rotating shaft. 図２における遠心ファンの入口設置角を説明する図である。It is a figure explaining the entrance installation angle of the centrifugal fan in FIG. 羽根の回転軸方向の高さと入口設置角度との対応関係を示すグラフである。It is a graph which shows the correspondence of the height of the rotation-axis direction of a blade | wing, and an inlet installation angle. 遠心ファンの主板側の前縁位置に対し、吸込み側の前縁位置の回転角度を説明する図である。It is a figure explaining the rotation angle of the front edge position by the side of suction to the front edge position by the side of the main plate of a centrifugal fan. 遠心ファンにおける吸い込み流量と羽根の回転角度の関係を示すグラフである。It is a graph which shows the relationship between the suction flow volume in a centrifugal fan, and the rotation angle of a blade | wing. 遠心ファンにおける羽根形状を示した図である。It is the figure which showed the blade | wing shape in a centrifugal fan. 本発明の遠心ファンを回転電機へ適用した説明した図である。It is the figure which applied the centrifugal fan of the present invention to a rotary electric machine. 本発明の実施の形態２に係る遠心ファンの羽根の説明図である。It is explanatory drawing of the blade | wing of the centrifugal fan which concerns on Embodiment 2 of this invention.
　以下、本発明の遠心ファンの実施の形態について、添付図面に基づいて説明する。 Hereinafter, an embodiment of a centrifugal fan of the present invention will be described based on the attached drawings.
　実施の形態１．
　図１は、本発明の実施の形態１に係る遠心ファン１の構成図である。遠心ファン１は、主板３と複数の羽根２とを備えている。主板３は、板状の形状であって、その中央に回転軸穴５が設けられている。主板３の回転軸穴５は、中心がお椀状に膨らんでいるような形状でもよい。また、主板３は、中央に回転させるためのシャフトを通すための穴を設けた形状でもよい。また、主板３は、強度面から、リブのような突起を設けた形状であってもよい。 Embodiment 1
FIG. 1 is a configuration diagram of a centrifugal fan 1 according to Embodiment 1 of the present invention. The centrifugal fan 1 includes a main plate 3 and a plurality of blades 2. The main plate 3 has a plate-like shape, and the rotation shaft hole 5 is provided at the center thereof. The rotation shaft hole 5 of the main plate 3 may have a shape in which the center is expanded like a bowl. Further, the main plate 3 may have a shape provided with a hole for passing a shaft for rotation to the center. Further, the main plate 3 may have a shape provided with a projection such as a rib from the strength surface.
　主板３の周方向には、間隔をおいて複数の翼４が放射状に設けられている。隣接する翼４の間には、切り欠きが設けられている。翼４には、回転軸方向に羽根２が設けられている。図１における矢印は、回転軸穴４を中心として、遠心ファンが回転する方向を示している。 A plurality of wings 4 are radially provided at intervals in the circumferential direction of the main plate 3. A notch is provided between adjacent wings 4. The wing 4 is provided on the wing 4 in the rotation axis direction. Arrows in FIG. 1 indicate directions in which the centrifugal fan rotates about the rotation shaft hole 4.
　羽根２において、回転軸側が羽根の前縁２ａ、羽根２の外縁部が羽根の後縁２ｂとする。羽根の前縁２ａは、遠心ファン１の回転方向に傾斜するように設けられている。すなわち、羽根２は、前縁２ａが主板３および翼４から離れるにつれて、遠心ファン１の回転方向に、次第にはやく回転することになる。 In the blade 2, the rotary shaft side is the front edge 2a of the blade, and the outer edge of the blade 2 is the rear edge 2b of the blade. The front edge 2 a of the blade is provided to be inclined in the rotational direction of the centrifugal fan 1. That is, as the leading edge 2 a moves away from the main plate 3 and the wing 4, the blades 2 will gradually rotate in the rotational direction of the centrifugal fan 1.
　また、羽根前縁２ａと回転軸を中心として前縁を通る円の円周方向とが成す角度を小さくすることで、羽根前縁での流れの衝突がなくなり、羽根で発生する騒音を小さくしつつ、羽根２の負圧面に生じる負圧をより小さくできる。さらに、主板３に切り欠きを設けることにより、回転軸方向へ流れる流量を増加させることができる。
この結果、図１に示した遠心ファンの構造により、流量を増加させることができる。 Also, by reducing the angle between the blade leading edge 2a and the circumferential direction of the circle passing through the leading edge about the rotation axis, there is no flow collision at the blade leading edge and noise generated by the blade is reduced. However, the negative pressure generated on the negative pressure surface of the blade 2 can be further reduced. Furthermore, by providing the main plate 3 with a notch, the flow rate flowing in the rotational axis direction can be increased.
As a result, the flow rate can be increased by the structure of the centrifugal fan shown in FIG.
　さらに、図２～図５を用いて、遠心ファン１の詳細について説明する。図２は、図１における遠心ファンを回転軸の垂直方向から見た断面図である。図３は、遠心ファンの入口設置角を説明する図である。図４は、遠心ファンの羽根の回転軸方向の高さと、入口設置角度との対応関係を示すグラフである。図５は、遠心ファンの主板側の前縁位置に対し、吸込み側の前縁位置の回転角度を説明する図である。 Further, the details of the centrifugal fan 1 will be described with reference to FIGS. FIG. 2 is a cross-sectional view of the centrifugal fan in FIG. 1 as viewed from the vertical direction of the rotation axis. FIG. 3 is a view for explaining the installation angle of the centrifugal fan. FIG. 4 is a graph showing the correspondence between the height in the rotational axis direction of the blades of the centrifugal fan and the inlet installation angle. FIG. 5 is a view for explaining the rotation angle of the leading edge position on the suction side with respect to the leading edge position on the main plate side of the centrifugal fan.
　なお、説明における羽根高さとは、遠心ファン１の回転軸方向に垂直な断面における羽根の高さをいうものとする。 The blade height in the description refers to the height of the blade in a cross section perpendicular to the rotational axis direction of the centrifugal fan 1.
　図２に示した羽根２において、紙面の上方向側が遠心ファン１の吸込み側であり、紙面の下方向側が主板３側である。羽根２の高さ方向に、遠心ファンの吸込み側から羽根高さＡ、Ｂ、Ｃの位置における断面を、それぞれ断面Ａ、断面Ｂ及び断面Ｃとする。 In the blade 2 shown in FIG. 2, the upper side of the drawing is the suction side of the centrifugal fan 1, and the lower side of the drawing is the main plate 3 side. Cross sections at positions of blade heights A, B and C from the suction side of the centrifugal fan in the height direction of the blades 2 are taken as a cross section A, a cross section B and a cross section C, respectively.
　図３の点線は、主板３における、切り欠きの根元部分での円周を表している。図３に示されるように、Ａ、Ｂ、Ｃの各高さでの断面内における羽根２の形状が、円周方向と成す角度を、それぞれ入口設置角度θA、入口設置角度θB、入口設置角度θCと設定する。 The dotted line in FIG. 3 represents the circumference of the main plate 3 at the root portion of the notch. As shown in FIG. 3, the shape of the blade 2 in the cross section at each height of A, B and C makes an angle with the circumferential direction as an inlet installation angle θ A , an inlet installation angle θ B , and an inlet Set as the installation angle θ C.
　図４には、羽根２の回転軸方向の高さと、入口設置角度との対応関係が示されている。縦軸は、羽根２の回転軸方向の高さを、羽根最大高さに対する比として表している。また、横軸は、入口設置角度θ［°］を表している。また、実線は、本願発明における対応関係を示しており、破線は、先行技術における対応関係を示している。 FIG. 4 shows the correspondence between the height of the blade 2 in the rotational axis direction and the inlet installation angle. The vertical axis represents the height of the blade 2 in the rotational axis direction as a ratio to the maximum blade height. The horizontal axis represents the inlet installation angle θ [°]. The solid line shows the correspondence in the present invention, and the broken line shows the correspondence in the prior art.
　本願発明では、入口設置角度θA、θB、θCの間には、θA＜θB、θC＜θBの関係が成り立っている。入口設置角度θBが最大になる断面Ｂの高さは、主板３から最大羽根高さの略２／３の高さまでの範囲内に設けることが望ましい。また、入口設置角度θAおよび入口設置角度θBについては、－１０≦θA≦３０、２０≦θB≦７０の範囲に設定することが望ましく、θCはθB未満の任意の角度でよい。 In the present invention, the relationship of θ A <θ B and θ C <θ B is established among the inlet installation angles θ A , θ B and θ C. The height of the cross section B of inlet installation angle theta B is maximized, it is desirable to provide in the range of from the main plate 3 to a height of approximately 2/3 of the maximum blade height. The inlet installation angle θ A and the inlet installation angle θ B are preferably set in the range of −10 ≦ θ A ≦ 30, 20 ≦ θ B ≦ 70, and θ C is an arbitrary angle less than θ B. Good.
　上記のように、主板３側の入口設置角度を小さくすることにより、羽根２に対して円周方向に流れる流量を低減させることができる。この結果、遠心ファン１の吸い込み側から主板３方向へ通過する流れと、円周方向の流れとの衝突が少なくなり、回転軸方向の流量を増加させることできる。
　実験の結果、本件の羽根２は、このような前縁形状を有することにより、先行技術である羽根２と比較して、流量が略１０％増加し、騒音値は、オーバーオール値で約０．３ｄＢ低減することができた。 As described above, the flow rate flowing in the circumferential direction with respect to the blades 2 can be reduced by reducing the inlet installation angle on the main plate 3 side. As a result, the collision between the flow passing from the suction side of the centrifugal fan 1 toward the main plate 3 and the flow in the circumferential direction decreases, and the flow rate in the rotational axis direction can be increased.
As a result of the experiment, the present blade 2 has such a leading edge shape, and the flow rate is increased by about 10% as compared with the blade 2 of the prior art, and the noise value is approximately 0. 0 in overall value. It could be reduced by 3 dB.
　本実施の形態１では、複数の羽根２において、入口設置角度θA、θB、θCのそれぞれが、全ての羽根で同一である場合について説明した。しかしながら、全ての羽根で同一の値を採用するのではなく、それぞれの羽根ごとに、θA＜θB、θC＜θBの関係が成立するようにして、個別の値を採用することも可能である。さらに、断面Ｂにおける入口設置角度θBが最も大きくなるが、高さＢは、それぞれの羽根２ごとに異なっていてもよい。 In the first embodiment, in the plurality of blades 2, the case where the inlet installation angles θ A , θ B , and θ C are the same for all the blades has been described. However, instead of adopting the same value for all the blades, it is also possible to adopt individual values such that the relationship of θ A <θ B and θ C <θ B is established for each blade. It is possible. Furthermore, although the inlet setting angle theta B in the section B becomes the largest, the height B may be different for each of the blades 2.
　上記のように、図４に示したように、羽根２の高さ方向に応じて、入口設置角度を変えることにより、遠心ファン１の風量を低減させることなく、遠心ファン１によって発生する回転騒音を変調させ、低騒音化させることができる。すなわち、本発明の遠心ファンは、低騒音化を図った上で、回転軸方向の流量を増加させる効果を実現できる。 As described above, as shown in FIG. 4, the rotational noise generated by the centrifugal fan 1 without reducing the air volume of the centrifugal fan 1 by changing the inlet installation angle according to the height direction of the blades 2 Can be modulated to reduce noise. That is, the centrifugal fan according to the present invention can realize the effect of increasing the flow rate in the direction of the rotation axis after noise reduction.
　図４に示されるように、羽根２の入口設置角度は、羽根２の高さ方向において、主板３側から吸込み側に少なくとも１回大きくなり、少なくとも１回小さくなるように設計されている。すなわち、入口設置角度は、羽根２の高さ方向において、ある高さＢにおいて１つの極値を有している。 As shown in FIG. 4, the inlet installation angle of the blades 2 is designed to increase at least once from the main plate 3 side to the suction side in the height direction of the blades 2 and decrease at least once. That is, the inlet installation angle has one extreme value at a certain height B in the height direction of the blade 2.
　図４では、羽根２の前縁の入口設置角度が主板側のＣ位置からＢ位置にかけて１回大きくなり、Ｂ位置から吸込み側のＡ位置にかけて１回小さくなり、Ｂ位置において入口設置角度に１つの極値を有している。ここで、Ｂ位置は、羽根最大高さに対する比が、０．４～０．５となっている。 In FIG. 4, the inlet installation angle of the front edge of the blade 2 increases once from C position to B position on the main plate side and decreases once from B position to A position on the suction side. It has one extremum. Here, in the position B, the ratio to the maximum blade height is 0.4 to 0.5.
　なお、羽根２の前縁の入口設置角度は、大きくなり、その後小さくなるということを複数回繰り返すように、複数の極値を有してもよい。 In addition, the inlet installation angle of the front edge of the blade | wing 2 may have several extreme value so that it may become large and it may become small after that several times.
　図５は、遠心ファンの吸込み側の前縁位置の回転角度を説明する図である。羽根２の前縁の回転中心軸からの半径は、略等しく、遠心ファン１の回転中心をＯとして、主板３側の前縁と吸込み側の前縁のなす角を回転角度ζ［°］と設定する。主板３側の前縁に対して、吸込み側の前縁が回転方向にζ°回転してもよい。 FIG. 5 is a diagram for explaining the rotation angle of the leading edge position on the suction side of the centrifugal fan. The radius from the rotation center axis of the front edge of the blade 2 is approximately equal, and the rotation angle ζ [°] is the angle between the front edge on the main plate 3 and the front edge on the suction side, where O is the rotation center of the centrifugal fan 1 Set The front edge on the suction side may be rotated about the front edge on the main plate 3 side in the rotational direction.
　図６は、遠心ファン１における流量と羽根の回転角度ζの関係を示すグラフである。縦軸が吸い込み流量の増減［％］を示しており、横軸が羽根の回転角度ζ［°］を示している。回転角度ζ［°］は、０°≦ζ≦１０°の範囲内において、小さくなると遠心ファンの吸い込み流量は増加し、大きくなると、遠心ファンの吸い込み流量は減少している。 FIG. 6 is a graph showing the relationship between the flow rate of the centrifugal fan 1 and the rotational angle 羽 根 of the blades. The vertical axis represents increase or decrease [%] of suction flow rate, and the horizontal axis represents blade rotation angle ζ [°]. When the rotation angle ζ [°] decreases within the range of 0 ° ζ 10 10 °, the suction flow rate of the centrifugal fan increases, and as it increases, the suction flow rate of the centrifugal fan decreases.
　回転角度ζを特に約７°以下とすることによって、遠心ファン１から発生する騒音を低減し、しかも吸い込み流量を増加させることができる
　また、羽根２の前縁については、円弧状に丸みを設けてもよい。 In particular, by setting the rotation angle ζ to about 7 ° or less, the noise generated from the centrifugal fan 1 can be reduced and the suction flow rate can be increased. Further, the front edge of the blade 2 is rounded in an arc shape. May be
　羽根２の断面形状は、図２に示される羽根２の回転軸方向の断面Ａ、Ｂ、Ｃにおいては、それぞれ異なっていた。これに対して、図７を用いて、別の羽根形状について説明する。 The cross-sectional shape of the blade | wing 2 was respectively different in cross-section A, B, C of the rotating shaft direction of the blade | wing 2 shown by FIG. On the other hand, another blade shape will be described with reference to FIG.
　図７は、遠心ファン１における羽根形状を示した図である。羽根２の前縁位置をＤ、羽根２の後縁位置をＦとする。さらに、羽根２の前縁位置Ｄと後縁位置Ｆとの間にある任意の位置をＥとする。この場合、羽根２の前縁位置Ｄから任意の位置Ｅまでの翼４の形状は、羽根の高さ方向によって異なり、羽根の任意の位置Ｅから後縁位置Ｆまでの翼４の形状は、羽根の全ての高さ方向において略同一になるように設計してもよい。 FIG. 7 is a view showing a blade shape of the centrifugal fan 1. The front edge position of the blade 2 is D, and the rear edge position of the blade 2 is F. Further, an arbitrary position between the front edge position D and the rear edge position F of the blade 2 is E. In this case, the shape of the blade 4 from the leading edge position D of the blade 2 to the arbitrary position E differs depending on the height direction of the blade, and the shape of the blade 4 from the arbitrary position E of the blade to the trailing edge position F is It may be designed to be substantially the same in all the height directions of the blades.
　本発明を適用した一実施例としての車両用交流発電機１００を図８に示す。車両用交流発電機１００は、本実施の形態１の遠心ファン８３と、ケーシング４と、一対のベアリング５と、シャフト６と、プーリ７と、回転子８と、固定子９と、スリップリング１０と、一対のブラシ１１と、電圧調整器１２と、整流装置１３と、ヒートシンク１８と、コネクタ２０と、保護カバー２７と、を備えている。 A vehicular AC generator 100 as one embodiment to which the present invention is applied is shown in FIG. The automotive alternator 100 includes the centrifugal fan 83, the casing 4, the pair of bearings 5, the shaft 6, the pulley 7, the rotor 8, the stator 9, and the slip ring 10 according to the first embodiment. , A pair of brushes 11, a voltage regulator 12, a rectifying device 13, a heat sink 18, a connector 20, and a protective cover 27.
　ケーシング４は、略椀形状のアルミニウム製のフロント側ハウジング３１、およびリヤ側ハウジング３０を備える。ケーシング４は、一対のベアリング５を介して回転自在に支持されたシャフト６を備える。ケーシング４のフロント側に延出したシャフト６の端部には、プーリ７が固着されている。ケーシング４内には、シャフト６と一体的に回転する回転子８が配設されている。 The casing 4 includes a substantially wedge-shaped front housing 31 made of aluminum and a rear housing 30. The casing 4 includes a shaft 6 rotatably supported via a pair of bearings 5. A pulley 7 is fixed to an end of the shaft 6 extending to the front side of the casing 4. In the casing 4, a rotor 8 that rotates integrally with the shaft 6 is disposed.
　回転子８の外周には、固定子９が対向配置され、また、固定子９は、ケーシング４に固定されている。ケーシング４のリヤ側に延出したシャフト６には、回転子８に電流を供給する一対のスリップリング１０が固定されている。各スリップリング１０の表面には、摺動する一対のブラシ１１と、これらのブラシ１１を収容しているブラシホルダ１７が設けられている。 The stator 9 is disposed opposite to the outer periphery of the rotor 8, and the stator 9 is fixed to the casing 4. A pair of slip rings 10 for supplying an electric current to the rotor 8 is fixed to the shaft 6 extended to the rear side of the casing 4. On the surface of each slip ring 10, a pair of sliding brushes 11 and a brush holder 17 accommodating the brushes 11 are provided.
　ブラシ１１に隣接するように、固定子９で生じた交流電圧の大きさを調整する電圧調整器１２と、固定子９で生じる交流電圧を直流電圧に整流する整流装置１３と、ヒートシンク１８と、電圧調整器１２と図示しない外部装置との信号の入出力を行うコネクタ２０とが設けられている。ブラシホルダ１７と整流装置１３を覆うように、保護カバー２７が設けられている。 A voltage regulator 12 for adjusting the magnitude of the AC voltage generated in the stator 9 adjacent to the brush 11, a rectifier 13 for rectifying the AC voltage generated in the stator 9 into a DC voltage, a heat sink 18; A connector 20 is provided to input and output signals between the voltage regulator 12 and an external device (not shown). A protective cover 27 is provided to cover the brush holder 17 and the rectifying device 13.
　回転子８は、界磁巻き線８１と界磁鉄芯８２により形成され、界磁巻き線を冷却するための通風路が備えられている。界磁鉄芯８２は、それぞれが６個あるいは８個の爪部を有し、界磁巻線８１を覆うように設けられている。 The rotor 8 is formed of a field winding 81 and a field iron core 82, and is provided with an air passage for cooling the field winding. Each of the field cores 82 has six or eight claws, and is provided so as to cover the field winding 81.
　界磁巻線８１は、ランデル型回転子であり、絶縁処理された銅線を円筒状かつ同心状に巻き回され、励磁電流が流れて磁束を発生する。界磁巻線８１が発生する磁束によって磁極が形成される。遠心ファン８３は、回転子８の両端面に溶接等により取り付けられている。 The field winding 81 is a Lundell-type rotor, and is wound cylindrically and concentrically with an insulated copper wire, and an excitation current flows to generate a magnetic flux. A magnetic pole is formed by the magnetic flux generated by the field winding 81. The centrifugal fan 83 is attached to both end surfaces of the rotor 8 by welding or the like.
　本発明の実施の形態１に係る遠心ファン８３を適用した車両用交流発電機１００の作用について、図９を用いて説明する。回転子８の回転により、回転子８に取り付けられた遠心ファン８３も、回転子８と一体に回転する。この結果、軸方向に流体が流れ、外気が車両用交流発電機１００内に吸引される。外気は、車両用交流発電機１００内の構成部品、特に界磁巻き線８１を冷却した後、外部に排出される。 The operation of the vehicular AC generator 100 to which the centrifugal fan 83 according to the first embodiment of the present invention is applied will be described with reference to FIG. Due to the rotation of the rotor 8, the centrifugal fan 83 attached to the rotor 8 also rotates integrally with the rotor 8. As a result, the fluid flows in the axial direction, and the outside air is sucked into the automotive alternator 100. The outside air cools the components in the automotive alternator 100, particularly the field winding 81, and then is discharged to the outside.
　遠心ファン８３を回転子８に備えることにより、低騒音化を図った上で、回転子内部の軸方向へ流れる流体を増加させ、冷却性能を向上させることができる。 By providing the centrifugal fan 83 in the rotor 8, it is possible to improve the cooling performance by increasing the fluid flowing in the axial direction inside the rotor after noise reduction is achieved.
　本発明の活用例として、このような車両用交流発電機に使用することが挙げられるが、本発明は、これに限定されるものではない。本発明は、例えば、車載用交流発電機、モータ、車載用駆動装置などの回転電機の回転子に取り付けて利用することもできる。 Although the example of application of the present invention is used for such a car alternator, the present invention is not limited to this. The present invention can also be used by attaching to, for example, a rotor of a rotating electrical machine such as an on-vehicle alternating current generator, a motor, or an on-vehicle drive device.
　実施の形態１による遠心ファンは、主板と、主板に設けられた複数の翼と、翼に設けられた羽根とを備えるとともに、羽根の前縁の入口設置角度を遠心ファンの回転軸方向の高さに応じて変化させている。具体的には、実施の形態１による遠心ファンは、主板側から吸込み側に向かうにつれて、羽根の前縁の入口設置角度が大きくなり、その後小さくなるようにして、入口設置角度に少なくとも１つの極値をもつ羽根を備える。 The centrifugal fan according to the first embodiment includes a main plate, a plurality of wings provided on the main plate, and a wing provided on the wing, and the inlet installation angle of the leading edge of the wing is set to a height in the rotational axis direction of the centrifugal fan Change according to the Specifically, in the centrifugal fan according to the first embodiment, the inlet installation angle of the leading edge of the blade increases and then decreases as it goes from the main plate side to the suction side, and then the inlet installation angle is at least one pole. It has a blade with a value.
　このような構成を備えることにより、遠心ファンの回転軸方向への流量を増加させることできる。従って、遠心ファンから発生する騒音を低騒音化させた上で、吸込み流量を増加させることができ、低騒音化と冷却性能の向上の両立を図ることができる。 By providing such a configuration, the flow rate in the rotational axis direction of the centrifugal fan can be increased. Therefore, after reducing the noise generated from the centrifugal fan, the suction flow rate can be increased, and both noise reduction and improvement of the cooling performance can be achieved.
　複数の羽根のそれぞれは、入口設置角度の極値を有する羽根高さを、異なる高さに設定することもできる。これにより、遠心ファンの回転軸方向への流量を、羽根毎に異なるように増加させることができる。さらに、羽根の形状が回転方向によって異なる。このため、ファンの風量を低減させることなく、遠心ファンの回転数に関係する騒音をその周辺の周波数へ分散させて変調させ、低騒音化させることができる。 Each of the plurality of vanes may have vane heights having extrema of the inlet installation angle set to different heights. Thereby, it is possible to increase the flow rate in the rotational axis direction of the centrifugal fan differently for each blade. Furthermore, the shape of the blades differs depending on the direction of rotation. For this reason, without reducing the air volume of the fan, noise related to the rotational speed of the centrifugal fan can be dispersed and modulated to the frequency around it to reduce noise.
　羽根の前縁は、遠心ファンの回転方向に傾斜している。このような羽根の構成により、羽根の前縁が主板および翼から離れるにつれて遠心ファンの回転方向に次第にはやく回転することになる。この結果、遠心ファンの回転数に関係する騒音をその周辺の周波数へ分散させて変調させ、低騒音化させることができる。 The leading edge of the blade is inclined in the direction of rotation of the centrifugal fan. Such a configuration of the blades causes the leading edge of the blades to rotate gradually and quickly in the direction of rotation of the centrifugal fan as it moves away from the main plate and the blades. As a result, noise related to the rotational speed of the centrifugal fan can be dispersed and modulated to frequencies around it to reduce noise.
　複数の羽根のそれぞれの遠心ファンの回転軸方向に垂直な断面において、前縁位置と後縁位置と、前縁位置と後縁位置の間にある翼の面上に任意の位置とを規定した際に、前縁位置から任意の位置までの曲線が羽根ごとで異なり、任意の位置から後縁位置までの曲線が少なくとも２つの羽根で等しくなるように、羽根を設計することができる。 In a cross section perpendicular to the rotational axis direction of each centrifugal fan of the plurality of blades, the front edge position and the rear edge position and an arbitrary position on the plane of the wing between the front edge position and the rear edge position In this case, the blades can be designed such that the curve from the leading edge position to the arbitrary position is different for each blade, and the curve from the arbitrary position to the trailing edge position is equal in at least two blades.
　このような構成を備えることで、羽根の前縁部の形状が羽根の高さ方向に異なることにより、羽根前縁部に存在する騒音源を効果的に低減することができる。この結果、遠心ファンから発生する騒音を低騒音化することができる。さらに、全ての羽根の後縁部の形状を、羽根の高さ方向において等しくすることにより、吸い込み流量の低下を抑制することができる。 By providing such a configuration, noise sources present at the leading edge of the blade can be effectively reduced by making the shape of the leading edge of the blade different in the height direction of the blade. As a result, the noise generated from the centrifugal fan can be reduced. Furthermore, by equalizing the shape of the trailing edge of all the vanes in the height direction of the vanes, it is possible to suppress a decrease in suction flow rate.
　主板側の前縁に対して、吸込み側の前縁の回転方向ζを、０≦ζ≦１０とする羽根を設計することができる。これにより、遠心ファンの吸込み流量を増加させることができ、冷却能力を向上させることができる。従って、低騒音化と冷却性能の向上の両立を図ることができる。 For the leading edge on the main plate side, a blade can be designed in which the rotational direction ζ of the leading edge on the suction side is 0 ≦ 0 ≦ 10. Thereby, the suction flow rate of the centrifugal fan can be increased, and the cooling capacity can be improved. Therefore, both noise reduction and improvement of the cooling performance can be achieved.
　また、本発明に係る遠心ファンは、回転電機に適用することができる。このような適用により、回転電機の回転軸方向へ流れる流量を増加させることができる。この結果、低騒音化と冷却性能の向上の両立を図る回転電機を実現することができる。 The centrifugal fan according to the present invention can be applied to a rotating electrical machine. Such an application can increase the flow rate flowing in the direction of the rotation shaft of the rotating electrical machine. As a result, it is possible to realize a rotating electrical machine that achieves both noise reduction and improvement in cooling performance.
　なお、本発明に係る遠心ファンは、上流側に位置して、羽根の主板と対向するように、円環状のシュラウドを備える構成を採用することも可能である。 The centrifugal fan according to the present invention can also be configured to include an annular shroud so as to be positioned upstream and face the main plate of the blade.
実施の形態２．
　本発明の実施の形態２に係る遠心ファン１の羽根１２の構成を図９に示す。なお、先の実施の形態１における図１～図８の参照符号と同一の符号は、同一又は同様の構成要素でり、その詳細な説明を省略する。 Second Embodiment
The structure of the blade | wing 12 of the centrifugal fan 1 which concerns on Embodiment 2 of this invention is shown in FIG. The same reference numerals as those in FIGS. 1 to 8 in the first embodiment denote the same or similar components, and a detailed description thereof will be omitted.
　図９に示すように、羽根２の前縁に任意の点Ｇを設定し、羽根２の吸込み側に任意の点Ｈを設定する。本実施の形態２に係る羽根２は、点Ｇと点Ｈを通過する直線により、回転方向に折り曲げるように傾斜させた構造を有している。 As shown in FIG. 9, an arbitrary point G is set at the front edge of the blade 2, and an arbitrary point H is set at the suction side of the blade 2. The blade 2 according to the second embodiment has a structure in which the blade 2 is inclined to be bent in the rotational direction by a straight line passing through the point G and the point H.
　このような傾斜構造を備えることで、羽根の前縁部に存在する騒音源を効果的に低減し、遠心ファンから発生する騒音を低騒音化できる。さらに、先の実施の形態１と同様に、遠心ファンの回転軸方向の流量を増加させることもできる。この結果、低騒音化と冷却性能の向上の両立を図った上で、先の実施の形態１よりも低騒音化の性能向上を実現できる。 By providing such an inclined structure, it is possible to effectively reduce the noise source present at the front edge of the blade and to reduce the noise generated from the centrifugal fan. Furthermore, as in the first embodiment, the flow rate in the rotational axis direction of the centrifugal fan can also be increased. As a result, while achieving both noise reduction and improvement in cooling performance, it is possible to realize performance improvement in noise reduction as compared to the first embodiment.
　１　遠心ファン、２　羽根、２a　羽根の前縁、２ｂ　羽根の後縁、３　主板、４　翼、５、回転軸の穴、６　シャフト、８　回転子、１００　回転電機、Ａ　羽根の高さ方向の吸込み側の位置、Ｂ　羽根の吸込み側の位置Ａと主板側の位置Ｃの間における任意の位置、Ｃ　羽根の高さ方向の主板側の位置、Ｄ　羽根の前縁位置、Ｅ　羽根の前縁と後縁の間における任意の点、Ｆ　羽根の後縁位置、Ｇ　羽根の前縁における任意の点、Ｈ　羽根の吸込み側の任意の点、Ｏ　回転中心、θA　羽根の高さＡの位置の入口設置角度、θB　羽根高さＢ位置の入口設置角度、θC　羽根高さＣ位置の入口設置角度、ζ　羽根前縁の回転角度。 1 Centrifugal fan, 2 blades, 2a blade leading edge, 2b blade trailing edge, 3 main plate, 4 blades, 5 rotary shaft holes, 6 shafts, 8 rotors, 100 rotary electric machines, A blade height direction Position on suction side, any position between position A on suction side of blade B and position C on side of main plate, position on main plate side in height direction of blade C, front edge position of blade D, front edge of blade E Any point between and the trailing edge, the trailing edge position of the F blade, any point at the leading edge of the G blade, any point on the suction side of the H blade, O center of rotation, height of the θ A blade Inlet installation angle of θ, Inlet installation angle of θ B blade height B position, Inlet installation angle of θ C blade height C position, Rotation angle of blade front edge.

Claims (7)

  1. 　主板と、主板に設けられた複数の翼と、前記複数の翼のそれぞれに設けられた複数の羽根とを備える遠心ファンであって、
    　前記複数の羽根のそれぞれにおいて、前記遠心ファンの回転軸側の端面を前縁部と規定し、前記前縁部における前記羽根の形状が、前記遠心ファンの円周方向と成す角度を入口設置角度と規定した際に、前記羽根は、前記遠心ファンの回転軸方向の高さに応じて前記入口設置角度が変化するように形成されており、かつ、前記羽根の主板側と吸込み側との間において、前記入口設置角度が最大となる極値を有するように形成されている
    　遠心ファン。     A centrifugal fan comprising a main plate, a plurality of blades provided on the main plate, and a plurality of blades provided on each of the plurality of blades,
    In each of the plurality of blades, an end face on the rotation shaft side of the centrifugal fan is defined as a front edge, and an angle between the shape of the blades at the front edge and the circumferential direction of the centrifugal fan is an inlet installation angle When defined as, the blade is formed so that the inlet installation angle changes according to the height of the centrifugal fan in the direction of the rotation axis, and between the main plate side and the suction side of the blade A centrifugal fan configured to have an extremum at which the inlet installation angle is at a maximum.
  2. 　前記複数の羽根のそれぞれは、前記極値を有する前記回転軸方向の羽根高さが個別に設定されている
    　請求項１に記載の遠心ファン。     The centrifugal fan according to claim 1, wherein each of the plurality of blades has a blade height in the direction of the rotation axis having the extreme value set individually.
  3. 　前記複数の羽根の少なくとも１つは、前記前縁部が前記遠心ファンの回転方向に傾斜して形成されている
    　請求項１に記載の遠心ファン。     The centrifugal fan according to claim 1, wherein at least one of the plurality of blades is formed such that the front edge portion is inclined in a rotational direction of the centrifugal fan.
  4. 　前記複数の羽根のそれぞれは、前記回転軸方向に垂直な断面において、前縁位置と、後縁位置と、前記前縁位置と前記後縁位置との間で前記翼の面上に任意の位置の３点を規定した際に、前記前縁位置から前記任意の位置までの曲線が羽根ごとで異なり、前記任意の位置から前記後縁位置までの曲線が少なくとも２つの羽根で等しくなるように形成されている
    　請求項１に記載の遠心ファン。     Each of the plurality of blades has any position on the surface of the wing between the leading edge position, the trailing edge position, the leading edge position and the trailing edge position in a cross section perpendicular to the rotation axis direction. When defining three points, the curve from the leading edge position to the arbitrary position is different for each blade, and the curve from the arbitrary position to the trailing edge position is formed to be equal in at least two blades. The centrifugal fan according to claim 1.
  5. 　前記複数の羽根の少なくとも１つは、前記前縁部における高さ方向の任意の点を第１点と規定し、前記羽根の吸込み側における前縁部と後縁部との間にある任意の点を第２点と規定した際に、前記第１点と前記第２点とを結ぶ直線に従って、前記羽根の前縁部における前記第１点以上の高さに相当する部分を遠心ファンの回転方向へ傾斜させるように形成されている
    　請求項１に記載の遠心ファン。     At least one of the plurality of blades defines any point in the height direction at the front edge as a first point, and any between the front edge and the rear edge on the suction side of the blades When a point is defined as a second point, according to a straight line connecting the first point and the second point, a portion corresponding to the height of the first point or more at the front edge of the blade is a centrifugal fan. The centrifugal fan according to claim 1, wherein the centrifugal fan is formed to be inclined in a direction.
  6. 　前記複数の羽根のそれぞれは、前記前縁部において、前記遠心ファンの回転中心軸と主板側の前縁部とを結ぶ直線と、前記回転中心軸と吸込み側の前縁部と結ぶ直線とが成す角度を回転角度ζと規定した際に、０≦ζ≦１０となるように形成されている請求項１に記載の遠心ファン。 Each of the plurality of blades has, at the front edge, a straight line connecting the central axis of rotation of the centrifugal fan and the front edge on the main plate side, and a straight line connecting the central axis of rotation and the front edge on the suction side The centrifugal fan according to claim 1, wherein when the angle formed is defined as a rotation angle ζ, 0ζ10.
  7. 　請求項１から６のいずれかに１項に記載の遠心ファンを回転子に備える回転電機。 A rotating electrical machine comprising the centrifugal fan according to any one of claims 1 to 6 in a rotor.
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