JP2008223741A - Centrifugal blower - Google Patents

Centrifugal blower Download PDF

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JP2008223741A
JP2008223741A JP2007067730A JP2007067730A JP2008223741A JP 2008223741 A JP2008223741 A JP 2008223741A JP 2007067730 A JP2007067730 A JP 2007067730A JP 2007067730 A JP2007067730 A JP 2007067730A JP 2008223741 A JP2008223741 A JP 2008223741A
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side plate
centrifugal blower
air
curvature
blades
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Toru Iwata
透 岩田
Akira Komatsu
彰 小松
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Daikin Industries Ltd
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Daikin Industries Ltd
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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
    • F04D29/281—Rotors specially for elastic fluids for centrifugal or helico-centrifugal pumps for radial-flow or helico-centrifugal pumps for fans or blowers
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F05—INDEXING SCHEMES RELATING TO ENGINES OR PUMPS IN VARIOUS SUBCLASSES OF CLASSES F01-F04
    • F05D—INDEXING SCHEME FOR ASPECTS RELATING TO NON-POSITIVE-DISPLACEMENT MACHINES OR ENGINES, GAS-TURBINES OR JET-PROPULSION PLANTS
    • F05D2250/00—Geometry
    • F05D2250/70—Shape

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)
  • Air-Conditioning Room Units, And Self-Contained Units In General (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide a centrifugal blower capable of effectively reducing exfoliation in the vicinity of a side plate of the centrifugal blower and improving air capacity and improving ventilation efficiency and reducing ventilation noises. <P>SOLUTION: In the centrifugal blower having a principal plate 14 and side plate 15, in which numerous blades 16, 16... between the principal plate 14 and side plate 15 are arranged circumferentially in parallel at a designated blade angle and designated blade intervals, a shape of an air guide surface of the side plate 15 opposing to the principal plate 14 is formed with an assembly of curved lines or straight lines and curved lines at the cross-section of the side plate 15 in the rotary shaft direction. A curvature of a curved line section is changed circumferentially, and the diameter at a peripheral edge of an air inlet and height in the shaft direction are set up to be fixed in the peripheral direction. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

本願発明は、遠心送風機の構造に関するものである。   The present invention relates to the structure of a centrifugal blower.

例えばターボファン等の遠心送風機は、円形の主板および漏斗形状の側板を有するとともに、これら主板および側板の間の空気流路に多数枚の羽根を所定の翼角、所定の翼間隔で周方向に並設して構成されている。   For example, a centrifugal fan such as a turbofan has a circular main plate and a funnel-shaped side plate, and a plurality of blades are arranged in the circumferential direction at a predetermined blade angle and a predetermined blade interval in the air flow path between the main plate and the side plate. It is configured.

このような遠心送風機の翼間流れは、多数枚の羽根の１ピッチ間で大きく変化する。しかし、同送風機の空気流路を形成する部材である上記主板と側板は、何れも周方向に一定の断面形状をなして構成されており、実際の翼間流れの変化に適切に対応していないため、特に側板面で剥離を生じ、性能を低下させていた。   The flow between the blades of such a centrifugal blower varies greatly between one pitch of many blades. However, both the main plate and the side plate, which are members forming the air flow path of the blower, are configured with a constant cross-sectional shape in the circumferential direction, and appropriately respond to actual changes in the flow between the blades. As a result, peeling occurred particularly on the side plate surface, which deteriorated the performance.

そこで、従来、上記側板の後縁形状を隣り合う羽根との間が傾斜面となるように周方向に階段状に変化させることによって、その静圧および風量に応じてインペラ内での剥離が生じやすい領域を減少させ、空気の流れを空気流路を形成している主板、側板および羽根の各表面に対して可及的滑らかに沿わせるようにしたものがある（特許文献１参照）。   Therefore, conventionally, by changing the trailing edge shape of the side plate in a stepwise manner in the circumferential direction so as to form an inclined surface between adjacent blades, peeling occurs in the impeller according to the static pressure and the air volume. There is one in which the easy area is reduced and the air flow is made to follow the surfaces of the main plate, the side plate, and the blades forming the air flow path as smoothly as possible (see Patent Document 1).

特開２００１−２６３２９４号公報（明細書１−７頁、図１−８）Japanese Patent Laid-Open No. 2001-263294 (Specification 1-7, FIG. 1-8)

しかし、この発明は、あくまでも特定の静圧および風量に応じて部分的に側板の後縁形状を階段状に変化させることによって剥離域を小さくしているのみであり、運転領域全体に亘って側板の隣り合う羽根間全体の断面形状を考慮したものではないので、必ずしも有効に剥離を低減することができなかった。   However, this invention only reduces the peeling area by partially changing the trailing edge shape of the side plate in a stepped manner in accordance with the specific static pressure and air volume, and the side plate over the entire operation area. Since the entire cross-sectional shape between adjacent blades is not taken into consideration, the peeling cannot always be effectively reduced.

また、羽根の負圧面側又は正圧面側の出口幅が狭くなり、吹き出し面積が小さくなる。   Further, the outlet width on the suction surface side or the pressure surface side of the blade is narrowed, and the blowing area is reduced.

もちろん、羽根の負圧面側の出口幅と正圧面側のではの一方を狭くしても、他方側を広くすることはできるが、その場合、羽根車の構造が複雑になり、送風効率の低下が懸念される。   Of course, even if one of the outlet width on the suction surface side of the blade and the pressure surface side is made narrower, the other side can be made wider, but in that case, the structure of the impeller becomes complicated and the blowing efficiency decreases. Is concerned.

そこで、本願発明では、同問題を解決するために、上記側板の前縁から後縁にいたる回転軸方向の断面の曲面を周方向に適切に所定の曲率で曲面状に変化させることにより、側板の羽根間各断面において、より剥離が生じにくい最適な流れを実現することによって、有効に送風音を抑制するとともに可及的に送風効率を向上させた遠心式送風機を提供することを目的とするものである。   Therefore, in the present invention, in order to solve the same problem, the side plate is changed by changing the curved surface of the cross section in the rotation axis direction from the front edge to the rear edge of the side plate appropriately into a curved shape with a predetermined curvature in the circumferential direction. An object of the present invention is to provide a centrifugal blower that effectively suppresses blowing noise and improves blowing efficiency as much as possible by realizing an optimum flow that is less likely to cause separation in each cross section between the blades Is.

本願発明は、同目的を達成するために、次のような課題解決手段を備えて構成されている。   In order to achieve the same object, the present invention is configured with the following problem solving means.

（１） 請求項１の発明
この発明は、主板１４および側板１５を有するとともに、これら主板１４および側板１５の間に多数枚の羽根１６，１６・・・を所定の翼角、所定の翼間隔で周方向に並設してなる遠心送風機であって、上記側板１５は、その回転軸方向の断面において、上記主板１４に対抗する気流ガイド面の形状が、曲線あるいは直線と曲線の組合せからなり、曲線部の曲率αが周方向に変化している一方、空気吸込口周縁の直径及び軸方向の高さが周方向に一定であることを特徴としている。 (1) The invention of claim 1 The present invention has a main plate 14 and side plates 15, and a plurality of blades 16, 16... The side plate 15 has a cross section in the direction of the rotation axis, and the shape of the air flow guide surface that opposes the main plate 14 is a curve or a combination of a straight line and a curve. While the curvature α of the curved portion changes in the circumferential direction, the diameter of the peripheral edge of the air suction port and the height in the axial direction are constant in the circumferential direction.

このような構成によると、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる翼間流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化することから、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the curved surface of the cross section in the rotation axis direction from the peripheral edge of the air suction port to the peripheral edge of the air outlet of the side plate is smooth with a different curvature in the circumferential direction corresponding to the change in the flow between the blades in the circumferential direction. Therefore, it is possible to realize an optimal flow that is less likely to cause separation in each circumferential section of the same side plate, effectively suppressing blowing noise and improving blowing efficiency. it can.

（２） 請求項２の発明
この発明は、上記請求項１の発明の構成において、側板１５の空気吹出口周縁と主板１４面との間の回転軸方向の距離が周方向に一定であることを特徴としている。 (2) Invention of Claim 2 This invention is the structure of the invention of said Claim 1, The distance of the rotating shaft direction between the air blower outlet periphery of the side plate 15 and the main plate 14 surface is constant in the circumferential direction. It is characterized by.

このような構成によると、側板１５の空気吹出口周縁と主板１４面との間の回転軸方向の距離が周方向に一定である遠心送風機において、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化するものとなり、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, in the centrifugal blower in which the distance in the rotation axis direction between the air blower peripheral edge of the side plate 15 and the main plate 14 surface is constant in the circumferential direction, the air blower peripheral edge from the air suction port peripheral edge of the side plate. The curved surface of the cross section in the direction of the rotation axis leads to a smoothly curved surface with a different curvature in the circumferential direction corresponding to the change in the flow in the circumferential direction, and more peeling in each circumferential section of the same side plate It is possible to realize an optimal flow that is less likely to occur, and to effectively suppress the blowing sound and improve the blowing efficiency.

（３） 請求項３の発明
この発明は、上記請求項１の発明の構成において、側板１５の空気吹出口周縁と主板１４面との間の回転軸方向の距離が周方向に変化していることを特徴としている。 (3) Invention of Claim 3 This invention is the structure of the said invention of Claim 1, The distance of the rotating shaft direction between the air blower outlet periphery of the side plate 15 and the main plate 14 surface has changed to the circumferential direction. It is characterized by that.

このような構成によると、側板１５の空気吹出口周縁と主板１４面との間の回転軸方向の距離が周方向に変化する状態で、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化するものとなり、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the distance in the rotation axis direction between the air outlet peripheral edge of the side plate 15 and the main plate 14 surface changes in the circumferential direction from the air inlet peripheral edge of the side plate to the air outlet peripheral edge. The curved surface of the cross section in the direction of the rotation axis changes smoothly into a curved surface with different curvatures in the circumferential direction in response to changes in the flow in the circumferential direction, and more peeling occurs in each circumferential section of the same side plate. It is possible to realize a difficult optimum flow, effectively suppressing the blowing sound and improving the blowing efficiency.

（４） 請求項４の発明
この発明は、上記請求項１，２又は３の発明の構成において、多数枚の羽根１６，１６・・・の１ピッチ間において、羽根１６，１６・・・の負圧面側と接する側板１５面の曲率αが最も大きいことを特徴としている。 (4) Invention of Claim 4 This invention is the structure of the said invention of Claim 1, 2, or 3 WHEREIN: Between 1 pitch of many blade | wings 16,16 ... of blade | wing 16,16 ... It is characterized in that the curvature α of the surface of the side plate 15 in contact with the suction surface side is the largest.

このような構成によると、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化することから、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the curved surface of the cross section in the rotation axis direction from the peripheral edge of the air suction port to the peripheral edge of the air outlet of the side plate is smoothly curved with a different curvature in the circumferential direction corresponding to the flow change in the circumferential direction. Therefore, in each circumferential section of the same side plate, it is possible to realize an optimal flow that is less likely to cause separation, and to effectively suppress the blowing sound and improve the blowing efficiency.

（５） 請求項５の発明
この発明は、上記請求項１，２又は３の発明の構成において、多数枚の羽根１６，１６・・・の１ピッチ間において、羽根１６，１６・・・の負圧面側と接する側板１５面の曲率αが最も大きく、正圧面側と接する側板１５面の曲率αが最も小さいことを特徴としている。 (5) Invention of Claim 5 This invention is the structure of the said invention of Claim 1, 2, or 3 WHEREIN: Between 1 pitch of many blade | wing 16,16 ... of blade | wing 16,16 ... The curvature α of the side plate 15 surface in contact with the suction surface side is the largest, and the curvature α of the side plate 15 surface in contact with the pressure surface side is the smallest.

このような構成によると、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化することから、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the curved surface of the cross section in the rotation axis direction from the peripheral edge of the air suction port to the peripheral edge of the air outlet of the side plate is smoothly curved with a different curvature in the circumferential direction corresponding to the flow change in the circumferential direction. Therefore, in each circumferential section of the same side plate, it is possible to realize an optimal flow that is less likely to cause separation, and to effectively suppress the blowing sound and improve the blowing efficiency.

（６） 請求項６の発明
この発明は、上記請求項１，２，３，４又は５の発明の構成において、側板１５の曲線部の曲率αが空気吹出口方向に少しづつ変化していることを特徴としている。 (6) Invention of Claim 6 This invention is the structure of the invention of the said Claim 1, 2, 3, 4 or 5, The curvature (alpha) of the curve part of the side plate 15 is changing little by little in the air blower outlet direction. It is characterized by that.

このような構成によると、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる流れの変化に対応して周方向に異なる曲率αで滑らかに曲面状に変化するものとなることから、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the curved surface of the cross section in the rotation axis direction from the air suction port periphery to the air blowout port periphery of the side plate is smoothly smooth with a curvature α different in the circumferential direction corresponding to the flow change in the circumferential direction. Since it changes to a curved surface, it is possible to achieve an optimal flow that is less prone to delamination in each circumferential section of the same side plate, effectively suppressing blowing noise and improving blowing efficiency. be able to.

（７） 請求項７の発明
この発明は、上記請求項１，２，３，４，５又は６の発明の構成において、多数枚の羽根１６，１６・・・のピッチが不等ピッチであり、側板１５の曲線部の曲率αの変化率が羽根１６，１６・・・のピッチ間で異なっていることを特徴としている。 (7) Invention of Claim 7 In the present invention, in the structure of the invention of Claim 1, 2, 3, 4, 5 or 6, the pitch of the plurality of blades 16, 16,... The change rate of the curvature α of the curved portion of the side plate 15 is different between the pitches of the blades 16, 16.

このような構成によると、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化するものとなることから、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the curved surface of the cross section in the rotation axis direction from the peripheral edge of the air suction port to the peripheral edge of the air outlet of the side plate is smoothly curved with a different curvature in the circumferential direction corresponding to the flow change in the circumferential direction. Therefore, it is possible to achieve an optimal flow that is less likely to cause separation in each circumferential section of the same side plate, effectively suppressing blowing noise and improving blowing efficiency. Can do.

（８） 請求項８の発明
この発明は、上記請求項７の発明の構成において、多数枚の羽根１６，１６・・・のピッチが不等ピッチであり、羽根１１全体の重心位置が回転軸上に重なるように側板１５の曲面形状が設定されていることを特徴としている。 (8) Invention of Claim 8 This invention is the structure of Claim 7 of this invention, The pitch of many blade | wings 16,16 ... is an unequal pitch, and the gravity center position of the blade | wing 11 whole is a rotating shaft. The curved surface shape of the side plate 15 is set so as to overlap therewith.

このような構成によると、上記側板の空気吸込口周縁から空気吹出口周縁にいたる回転軸方向の断面の曲面が、周方向においてなる流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化するものとなることから、同側板の周方向の各断面において、より剥離が生じにくい最適な流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the curved surface of the cross section in the rotation axis direction from the peripheral edge of the air suction port to the peripheral edge of the air outlet of the side plate is smoothly curved with a different curvature in the circumferential direction corresponding to the flow change in the circumferential direction. Therefore, it is possible to achieve an optimal flow that is less likely to cause separation in each circumferential section of the same side plate, effectively suppressing blowing noise and improving blowing efficiency. Can do.

（９） 請求項９の発明
この発明は、上記請求項１，２，３，４，５，６，７又は８の発明の構成において、空気調和機用室内機の送風機として構成されていることを特徴としている。 (9) Invention of Claim 9 This invention is configured as a blower for an indoor unit for an air conditioner in the configuration of the invention of Claim 1, 2, 3, 4, 5, 6, 7 or 8 above. It is characterized by.

このような構成によると、上記請求項１，２，３，４，５，６，７又は８の発明の構成により、空気調和機用の室内機として最適な、送風音が低く、送風効率の高い高性能の遠心送風機を実現することができる。   According to such a configuration, according to the configuration of the first, second, third, fourth, fifth, sixth, seventh, or eighth aspect of the present invention, the air blowing sound that is optimum as an indoor unit for an air conditioner is low, and the air blowing efficiency is low. A high-performance centrifugal blower can be realized.

以上の結果、本願発明によると、側板近傍における翼間流れの剥離を有効に低減し、効果的に風量の向上、送風効率の向上、送風音の低減を図ることが出来る。   As a result, according to the present invention, it is possible to effectively reduce the separation of the flow between the blades in the vicinity of the side plate, and to effectively improve the air volume, improve the blowing efficiency, and reduce the blowing sound.

したがって、空気調和機用の室内機に最適な低騒音・高性能の遠心送風機を提供することが可能となる。   Therefore, it is possible to provide a low-noise and high-performance centrifugal fan that is optimal for indoor units for air conditioners.

（最良の実施の形態１）
図１〜図７は、例えば天井埋込型空気調和機に適用した本願発明の最良の実施の形態１に係る遠心送風機の構造を示している。この場合、遠心送風機として、例えばターボファンが採用されている。 (Best Embodiment 1)
FIGS. 1-7 has shown the structure of the centrifugal blower which concerns on the best Embodiment 1 of this invention applied to the ceiling-embedded air conditioner, for example. In this case, for example, a turbo fan is employed as the centrifugal blower.

図１中、先ず符号２は、当該天井埋込型空気調和機１のカセット型の本体ケーシングである。該本体ケーシング２は、その吸気・吹出パネル（下面パネル部）４が天井３と略同一平面状に連続するようにして、天井３内に埋設されている。   In FIG. 1, reference numeral 2 is a cassette-type main body casing of the ceiling-embedded air conditioner 1. The main body casing 2 is embedded in the ceiling 3 such that its intake / blowout panel (lower surface panel portion) 4 continues in substantially the same plane as the ceiling 3.

そして、上記本体ケーシング２の上記吸気・吹出パネル４には、中央部に方形の空気吸込口５が設けられ、さらに、その内側に遠心ファンの一例であるターボファン１１用のベルマウス６が連設されている。   The intake / blowout panel 4 of the main casing 2 is provided with a square air inlet 5 at the center, and further, a bell mouth 6 for a turbo fan 11, which is an example of a centrifugal fan, is connected to the inside thereof. It is installed.

また、上記本体ケーシング２の吸気・吹出パネル４の上記空気吸込口５の外周部４方には、所定の幅の空気吹出口９，９・・が設けられている。   Further, air blowout ports 9, 9... Having a predetermined width are provided on the outer peripheral portion 4 side of the air suction port 5 of the intake / blowout panel 4 of the main body casing 2.

そして、上記本体ケーシング２内には上記空気吸込口５から上記ベルマウス６を経て上記空気吹出口９，９・・方向に到る全周方向の通風路１０が形成されており、該通風路１０の上記ベルマウス６の背後（図示上部）中央に位置して、その空気吸込側（後述する側板１５側）が上記ベルマウス６に対応するターボファン（遠心送風機）１１がファンモータ１３およびファンモータ１３の回転駆動軸１３ａを介して上記本体ケーシング２の天板２ａに吊設されている。   In the main body casing 2, a ventilation path 10 is formed in the entire circumferential direction from the air suction port 5 through the bell mouth 6 to the air outlets 9, 9. The turbo fan (centrifugal blower) 11 is located in the center of the rear of the bell mouth 6 (upper part in the figure) 10 and the air suction side (side plate 15 side described later) corresponds to the bell mouth 6 is a fan motor 13 and a fan. The main body casing 2 is suspended from the top plate 2 a via a rotation drive shaft 13 a of the motor 13.

また、同通風路１０には、該ターボファン１１を囲む状態で空気熱交換器１２が設けられている。   In addition, an air heat exchanger 12 is provided in the ventilation path 10 so as to surround the turbofan 11.

一方、該ターボファン１１は、上記ファンモータ１３の回転駆動軸１３ａに対して固定された円形の主板１４とターボファン羽根車内遠心方向への空気吸込口を形成する他端側漏斗形状の側板１５との間の空気流路に多数枚の羽根（動翼羽根）１６，１６・・・を所定の翼角、所定の翼間隔（不等ピッチ）で周方向に並設して構成されている。他方、その側板１５の筒状の空気吸込口側（図２〜図４では、上端側）周縁部内側には、上記ベルマウス６の下流側筒状の空気吹出口側周縁部が所定の隙間を保って相対回転可能に所定寸法遊嵌されている。   On the other hand, the turbo fan 11 includes a circular main plate 14 fixed to the rotational drive shaft 13a of the fan motor 13 and a funnel-shaped side plate 15 on the other end side that forms an air suction port in the centrifugal direction in the turbo fan impeller. Are arranged in parallel in the circumferential direction with a predetermined blade angle and a predetermined blade interval (unequal pitch). . On the other hand, on the inner side of the cylindrical air inlet side (the upper end side in FIGS. 2 to 4) of the side plate 15, a downstream cylindrical air outlet side peripheral portion of the bell mouth 6 has a predetermined gap. And is loosely fitted with a predetermined dimension so as to be relatively rotatable.

上記ベルマウス６は、上記ターボファン羽根車の空気吸込口を形成している上記側板１５の空気吸込口側周縁部に対して上記本体ケーシング２側空気吸込口５からの空気を羽根車内遠心方向にスムーズに流入させるために、図示のように吸気・吹出パネル４への取付縁部から内方に延び、その空気流上流側から空気流下流側にかけて次第に開口径が縮小した所定曲率半径の空気流入口部と空気流出口部とからなる気流ガイド面を有して構成されている。   The bell mouth 6 sends the air from the air inlet 5 on the side of the main body casing 2 to the peripheral edge of the air inlet of the side plate 15 forming the air inlet of the turbofan impeller. In order to smoothly flow in, air having a predetermined curvature radius that extends inwardly from the mounting edge to the intake / blowout panel 4 as shown in the figure, and whose opening diameter gradually decreases from the air flow upstream side to the air flow downstream side. It has an airflow guide surface composed of an inlet and an air outlet.

そして、その形状により上記ターボファン羽根車の側板１５に対応して、上記ターボファン羽根車の空気吸込側の空気を当該空気吸込側において空気吹出側遠心方向にスムーズにガイドすることによって、送風時に生じる空力騒音を可能な限り低減するようにしている。   And by corresponding to the side plate 15 of the turbo fan impeller by its shape, the air on the air suction side of the turbo fan impeller is smoothly guided in the air blowing side centrifugal direction on the air suction side, so that at the time of blowing The generated aerodynamic noise is reduced as much as possible.

ところで、この実施の形態の場合、上記側板１５は、例えば図４〜図７に示すように、その回転軸方向の断面において、当該側板１５の空気吹出口側周縁１５ｂと主板１４面との間の回転軸方向の距離（空気吹出口の高さＨ）が周方向に一定であり、かつ上記主板１４に対抗する気流ガイド面の形状が、直線部ａと曲線部ｂとの組合せからなり、曲線部ｂの曲率αが図６および図７に示すように周方向にα1〜α2〜α3と変化している一方、空気吸込口側周縁（直線部ａの始端）１５ａの直径Ｒ1及び空気吹出口側周縁（曲線部終端）１５ｂの直径Ｒ2並びに回転軸方向の高さ（空気吹出口の高さ）Ｈが周方向に一定となっている。 By the way, in the case of this embodiment, the said side plate 15 is between the air blower outlet side peripheral edge 15b of the said side plate 15, and the main plate 14 surface in the cross section of the rotating shaft direction, as shown, for example in FIGS. The distance in the rotational axis direction (height H of the air outlet) is constant in the circumferential direction, and the shape of the airflow guide surface that opposes the main plate 14 is a combination of the straight portion a and the curved portion b. As shown in FIGS. 6 and 7, the curvature α of the curved portion b changes in the circumferential direction from α 1 to α 2 to α 3 , while the diameter R of the air suction side peripheral edge (starting end of the straight portion a) 15a. 1 and air outlet side peripheral (curved portion terminating) 15b diameter R 2 and the rotation axis direction of the height of (the air outlet height) H is constant in the circumferential direction.

そして、例えば図６および図７に示すように、上記多数枚の羽根１６，１６・・・の１ピッチ間において、上記羽根１６，１６・・・の負圧面側と接する側板１５面の曲率α3が最も大きく、正圧面側と接する側板１５面の曲率α1が最も小さく形成されている。 And, for example, as shown in FIGS. 6 and 7, the curvature α of the surface of the side plate 15 in contact with the suction surface side of the blades 16, 16... 3 is the largest, and the curvature α 1 of the side plate 15 surface in contact with the pressure surface side is the smallest.

また、上記多数枚の羽根１６，１６・・・のピッチは不等ピッチであり、側板１５の曲線部ｂの曲率αが空気吸込口から空気吹出口方向にかけて少しづつ変化しており、上記側板１５の曲線部ｂの断面の曲率αの変化率が羽根１６，１６・・・のピッチ間で異なっている。   Further, the pitch of the plurality of blades 16, 16,... Is unequal, and the curvature α of the curved portion b of the side plate 15 changes little by little from the air inlet to the air outlet, The rate of change of the curvature α of the cross section of the 15 curved portions b is different between the pitches of the blades 16, 16.

このような構成によると、上記側板１５の空気吸込口周縁１５ａから空気吹出口側周縁１５ｂにいたる回転軸方向の断面（図６）の曲面が、周方向において異なる翼間流れの変化に対応して周方向に異なる曲率で滑らかに曲面状に変化するようになることから、同側板１５の周方向の各断面において、より剥離が生じにくい最適な翼間流れを実現することができ、効果的に送風音を抑制するとともに送風効率を向上させることができる。   According to such a configuration, the curved surface of the cross-section in the rotation axis direction (FIG. 6) from the air inlet peripheral edge 15a of the side plate 15 to the air outlet peripheral edge 15b corresponds to a change in the flow between the blades that differs in the circumferential direction. Therefore, it is possible to realize an optimum inter-blade flow that is less likely to cause separation in each circumferential cross section of the same side plate 15 because it smoothly changes to a curved surface with different curvatures in the circumferential direction. In addition, air blowing noise can be suppressed and air blowing efficiency can be improved.

なお、図１〜図３の構成では、その図面の表現形態において、上記側板１５の周方向の曲率αの変化（α1〜α2〜α3の相違）を示すことが困難なために、特に曲率αの変化が分るようには表現できていないが、実際には上述のように変化している。 In the configuration of FIGS. 1 to 3, in the representation form of the drawings, it is difficult to show changes in the curvature α in the circumferential direction of the side plate 15 (differences in α 1 to α 2 to α 3 ). In particular, it cannot be expressed so that the change in the curvature α can be seen, but it actually changes as described above.

（最良の実施の形態２）
次に図８および図９は、本願発明の最良の実施の形態２に係る遠心送風機の側板の要部の構成を示している。 (Best Mode 2)
Next, FIG. 8 and FIG. 9 show the configuration of the main part of the side plate of the centrifugal blower according to the second preferred embodiment of the present invention.

この実施の形態の側板１５でも、上記最良の実施の形態１のものと同様に、その回転軸方向の断面において、上記主板１４に対抗する気流ガイド面の形状が、やはり直線部ａと曲線部ｂの組合せからなり、その内の曲線部ｂの曲率αが周方向に変化しているが、同実施形態では、その場合において、さらに同側板１５の空気吹出口側周縁１５ｂと主板１４面との間の回転軸方向の距離（空気吹出口の高さＨ）をも周方向に変化（Ｈ1〜Ｈ2〜Ｈ3）させながら、上記曲線部ｂの曲率αを周方向に変化（α1〜α2〜α3）させたことを特徴とするものである。 Also in the side plate 15 of this embodiment, the shape of the airflow guide surface that opposes the main plate 14 in the cross section in the direction of the rotation axis is the straight portion a and the curved portion, as in the best embodiment 1. b, and the curvature α of the curved portion b thereof changes in the circumferential direction. In this embodiment, however, in that case, the air outlet side peripheral edge 15b of the same side plate 15 and the surface of the main plate 14 The curvature α of the curved portion b is changed in the circumferential direction while the distance in the rotation axis direction (height H of the air outlet) is also changed in the circumferential direction (H 1 to H 2 to H 3 ). 1 to α 2 to α 3 ).

このような構成の場合、羽根１６の空気吹出口側周縁１５ｂの正圧面側と負圧面側との間では階段状の段部が生じるが、隣合う羽根１６と羽根１６との間における空気吹出口側周縁１５ｂを含む側板１５の全体（直線部ａを除く部分）が周方向の吹出流れの相異に応じて周方向に曲率αを異にする最適な曲面形状となるので、上記最良の実施の形態１の場合よりも、より効果的に剥離を抑制することができるようになる。   In such a configuration, a stepped step portion is formed between the pressure surface side and the suction surface side of the air blower outlet side peripheral edge 15 b of the blade 16, but the air blowing between the adjacent blade 16 and the blade 16 is performed. The entire side plate 15 (portion excluding the straight portion a) including the outlet side peripheral edge 15b has an optimal curved surface shape having a different curvature α in the circumferential direction according to the difference in the circumferential blowout flow. Separation can be more effectively suppressed than in the case of the first embodiment.

（最良の実施の形態３）
次に図１０〜図１２は、本願発明の最良の実施の形態３に係る遠心送風機の羽根車部の構成を示している。 (Best Mode 3)
Next, FIGS. 10 to 12 show the configuration of the impeller part of the centrifugal blower according to the third preferred embodiment of the present invention.

この実施の形態の側板１５では、上記最良の実施の形態２のものと同様に、その回転軸方向の断面において、上記主板１４に対抗する気流ガイド面の形状が、直線部ａと曲線部ｂの組合せからなり、曲線部ｂの曲率αが周方向に変化しており、さらに側板１５の空気吹出口側周縁１５ｂと主板１４面との間の回転軸方向の距離をも図示のごとく周方向に変化させながら、上記曲線部ｂの曲率αを周方向に変化（α1〜α2〜α3）させてはいるが、特に羽根１６の空気吹出口側周縁１５ｂの正圧面側と負圧面側との間で階段状の段部が生じないように、可能な限り滑らかな曲面変化としたことを特徴とするものである。 In the side plate 15 of this embodiment, the shape of the airflow guide surface that opposes the main plate 14 in the cross section in the direction of the rotation axis is the straight portion a and the curved portion b, as in the best embodiment 2. The curvature α of the curved portion b changes in the circumferential direction, and the distance in the rotation axis direction between the air outlet side peripheral edge 15b of the side plate 15 and the surface of the main plate 14 is also circumferential as shown in the figure. While the curvature α of the curved portion b is changed in the circumferential direction (α 1 to α 2 to α 3 ), the pressure surface side and the suction surface of the air outlet side peripheral edge 15b of the blade 16 are particularly changed. It is characterized in that the curved surface changes as smoothly as possible so that a stepped step portion does not occur between the sides.

このような構成によれば、隣合う羽根１６と羽根１６との間における空気吹出口側周縁１５ｂを含む側板１５の全体（直線部ａを除く部分）が周方向の吹出流れの相異に応じて周方向に曲率αを異にする最適な曲面形状となるので、上記最良の実施の形態２の場合よりも、より効果的に剥離を抑制することができるようになる。   According to such a configuration, the entire side plate 15 (the portion excluding the straight portion a) including the air outlet side peripheral edge 15b between the adjacent blades 16 corresponds to the difference in the circumferential blow-out flow. Thus, the optimum curved surface shape having a different curvature α in the circumferential direction is obtained, and therefore, it is possible to more effectively suppress the peeling than in the case of the best embodiment 2.

しかも、同構成では、そのようにした場合においても、空気吹出口の高さＨを十分に大きく取ることができ、従来のように上記羽根１６，１６・・・の負圧面側又は正圧面側の出口幅が相当に狭くなり、空気吹出流路の吹き出し面積が小さくなるといった問題も生じにくい。   Moreover, in the same configuration, even in such a case, the height H of the air outlet can be made sufficiently large, and the pressure surface side or pressure surface side of the blades 16, 16. The outlet width of the air outlet becomes considerably narrow, and the problem that the blowing area of the air blowing passage becomes small hardly occurs.

（最良の実施の形態４）
次に図１３は、本願発明の最良の実施の形態４に係る遠心送風機の側板部の構成を示している。 (Fourth Embodiment)
Next, FIG. 13 shows the configuration of the side plate portion of the centrifugal fan according to the fourth embodiment of the present invention.

この実施の形態の側板１５では、上記最良の実施の形態３のものと同様に、その回転軸方向の断面において、上記主板１４に対抗する気流ガイド面の形状が、直線部ａと曲線部ｂの組合せからなり、曲線部ｂの曲率αが周方向に変化しており、さらに側板１５の空気吹出口側周縁１５ｂと主板１４面との間の回転軸方向の距離（空気吹出口の高さＨ）をも周方向に変化（Ｈ1〜Ｈ2〜Ｈ3）させながら、しかも上記曲線部ｂの曲率αを周方向に変化させ、かつ、できるだけ上記羽根１６，１６・・・の空気吹出口側周縁１５ｂの正圧面側と負圧面側との間で階段状の段部が生じないようにし、しかも、空気吹出口の高さＨ（換言すると、空気吹出流路の吹き出し面積）が可及的に大きくなるように周方向に曲率αを変化させたことを特徴とするものである。 In the side plate 15 of this embodiment, the shape of the airflow guide surface that opposes the main plate 14 in the cross section in the direction of the rotation axis is the straight portion a and the curved portion b, as in the best embodiment 3. The curvature α of the curved portion b is changed in the circumferential direction, and the distance in the rotation axis direction between the air outlet side peripheral edge 15b of the side plate 15 and the surface of the main plate 14 (height of the air outlet) H) is also changed in the circumferential direction (H 1 to H 2 to H 3 ), and the curvature α of the curved portion b is changed in the circumferential direction, and the air blowing of the blades 16, 16. A stepped step is not formed between the pressure surface side and the suction surface side of the outlet side peripheral edge 15b, and the height H of the air outlet (in other words, the blowing area of the air outlet passage) is possible. The curvature α is changed in the circumferential direction so as to increase as much as possible. Than is.

このような構成によれば、隣合う羽根１６と羽根１６との間における空気吹出口側周縁１５ｂを含む側板１５の全体（直線部ａを除く部分）が周方向の吹出流れの相異に応じて周方向に曲率αを異にする最適な曲面形状となるので、やはり上記最良の実施の形態２の場合よりも、より効果的に剥離を抑制することができるようになる。   According to such a configuration, the entire side plate 15 (the portion excluding the straight portion a) including the air outlet side peripheral edge 15b between the adjacent blades 16 corresponds to the difference in the circumferential blow-out flow. Thus, since the curved surface has an optimum curved shape with a different curvature α in the circumferential direction, it is possible to more effectively suppress the peeling than in the case of the second embodiment.

しかも、同構成では、図１３から明らかなように、空気吹出口の高さＨを周方向の広い角度範囲（１ピッチ間の略全域）に亘って高くすることができ、上述した羽根１６，１６・・・の負圧面側又は正圧面側の出口幅が狭くなり、空気吹出流路の吹き出し面積が小さくなる従来の問題を、より効果的かつ確実に解消することができる。   Moreover, in the same configuration, as is clear from FIG. 13, the height H of the air outlet can be increased over a wide angular range in the circumferential direction (substantially the entire area between one pitch). It is possible to more effectively and surely solve the conventional problem that the outlet width on the negative pressure surface side or the positive pressure surface side of 16...

天井埋込型空気調和機に適用した本願発明の最良の実施の形態１に係る遠心ファンおよび同遠心ファンを適用して構成した空気調和機の構成を示す断面図である。It is sectional drawing which shows the structure of the air conditioner comprised by applying the centrifugal fan which concerns on the best Embodiment 1 of this invention applied to the ceiling embedded type air conditioner, and the centrifugal fan. 同遠心ファンの羽根車の斜視図である（この場合、図１とは上下を逆にして示している。以下の各図においても同じ）。FIG. 2 is a perspective view of the impeller of the centrifugal fan (in this case, it is shown upside down from FIG. 1; the same applies to the following drawings). 同遠心ファンの羽根車の羽根部の拡大側面図である。It is an enlarged side view of the blade | wing part of the impeller of the centrifugal fan. 同遠心ファンの羽根車の羽根の構成を示す一部拡大断面図である。It is a partially expanded sectional view which shows the structure of the impeller of the centrifugal fan. 同遠心ファンの側板と羽根との関係を示す平面図である。It is a top view which shows the relationship between the side plate and blade | wing of the centrifugal fan. 同遠心送風機の側板の構成を示す説明用の断面図である。It is sectional drawing for description which shows the structure of the side plate of the centrifugal blower. 同遠心送風機の側板の周方向における曲率αの羽根間の変化と出口側の高さＨとの関係を示す図である。It is a figure which shows the relationship between the change between the blade | wings of the curvature (alpha) in the circumferential direction of the side plate of the centrifugal blower, and the height H on the exit side. 天井埋込型空気調和機に適用した本願発明の最良の実施の形態２に係る遠心送風機の側板の構成を示す説明用断面図である。It is sectional drawing for description which shows the structure of the side plate of the centrifugal blower which concerns on the best Embodiment 2 of this invention applied to the ceiling embedded type air conditioner. 同遠心送風機の側板の周方向における曲率半径αの羽根間の変化と出口側の高さＨとの関係を示す図である。It is a figure which shows the relationship between the change between the blade | wings of the curvature radius (alpha) in the circumferential direction of the side plate of the centrifugal blower, and the height H on the exit side. 本願発明の最良の実施の形態３に係る遠心送風機の羽根車の構成を示す斜視図である。It is a perspective view which shows the structure of the impeller of the centrifugal blower which concerns on best Embodiment 3 of this invention. 同遠心送風機の羽根車の羽根部の側面図である。It is a side view of the blade | wing part of the impeller of the centrifugal blower. 同遠心送風機の側板の周方向における曲率半径αの羽根間の変化と出口側の高さＨとの関係を示す図である。It is a figure which shows the relationship between the change between the blade | wings of the curvature radius (alpha) in the circumferential direction of the side plate of the centrifugal blower, and the height H on the exit side. 本願発明の最良の実施の形態４に係る遠心送風機の側板の周方向における曲率半径αの羽根間の変化と出口側の高さＨとの関係を示す図である。It is a figure which shows the relationship between the change between the blade | wings of the curvature radius (alpha) in the circumferential direction of the side plate of the centrifugal blower which concerns on best Embodiment 4 of this invention, and the height H of an exit side.

符号の説明Explanation of symbols

６はベルマウス、１０は通風路、１１はターボファン、１４は主板、１４ａはハブ、１５は側板、１６は羽根である。   6 is a bell mouth, 10 is a ventilation path, 11 is a turbo fan, 14 is a main plate, 14a is a hub, 15 is a side plate, and 16 is a blade.

Claims (9)

主板（１４）および側板（１５）を有するとともに、これら主板（１４）および側板（１５）の間に多数枚の羽根（１６），（１６）・・・を所定の翼角、所定の翼間隔で周方向に並設してなる遠心送風機であって、上記側板（１５）は、その回転軸方向の断面において、上記主板（１４）に対抗する気流ガイド面の形状が、曲線あるいは直線と曲線の組合せからなり、曲線部の曲率αが周方向に変化している一方、空気吸込口周縁の直径及び軸方向の高さが周方向に一定であることを特徴とする遠心送風機。   A main plate (14) and a side plate (15) are provided, and a plurality of blades (16), (16)... Are arranged between the main plate (14) and the side plate (15) with a predetermined blade angle and a predetermined blade interval. The side plate (15) has a cross section in the direction of the rotation axis, and the shape of the airflow guide surface that opposes the main plate (14) is a curve or a straight line and a curve. A centrifugal blower characterized in that the curvature α of the curved portion changes in the circumferential direction, while the diameter of the peripheral edge of the air inlet and the height in the axial direction are constant in the circumferential direction. 側板（１５）の空気吹出口周縁と主板（１４）面との間の回転軸方向の距離が周方向に一定であることを特徴とする請求項１記載の遠心送風機。   The centrifugal blower according to claim 1, wherein the distance in the rotation axis direction between the air outlet peripheral edge of the side plate (15) and the surface of the main plate (14) is constant in the circumferential direction. 側板（１５）の空気吹出口周縁と主板（１４）面との間の回転軸方向の距離が周方向に変化していることを特徴とする請求項１記載の遠心送風機。   The centrifugal blower according to claim 1, wherein the distance in the rotation axis direction between the air outlet peripheral edge of the side plate (15) and the surface of the main plate (14) changes in the circumferential direction. 多数枚の羽根（１６），（１６）・・・の１ピッチ間において、羽根（１６），（１６）・・・の負圧面側と接する側板（１５）面の曲率αが最も大きいことを特徴とする請求項１，２又は３記載の遠心送風機。   In one pitch of a large number of blades (16), (16)..., The curvature α of the side plate (15) surface in contact with the suction surface side of the blades (16), (16). The centrifugal blower according to claim 1, 2, or 3. 多数枚の羽根（１６），（１６）・・・の１ピッチ間において、羽根（１６），（１６）・・・の負圧面側と接する側板（１５）面の曲率αが最も大きく、正圧面側と接する側板（１５）面の曲率αが最も小さいことを特徴とする請求項１，２又は３記載の遠心送風機。   In one pitch of a large number of blades (16), (16)..., The curvature α of the side plate (15) surface contacting the suction surface side of the blades (16), (16). The centrifugal blower according to claim 1, 2, or 3, wherein the curvature α of the surface of the side plate (15) in contact with the pressure side is the smallest. 側板（１５）の曲線部の曲率αが空気吸込口から空気吹出口方向に変化していることを特徴とする請求項１，２，３，４又は５記載の遠心送風機。   The centrifugal blower according to claim 1, 2, 3, 4 or 5, characterized in that the curvature α of the curved portion of the side plate (15) changes from the air suction port toward the air blowout port. 多数枚の羽根（１６），（１６）・・・のピッチが不等ピッチであり、側板（１５）の曲線部の曲率αの変化率が羽根（１６），（１６）・・・のピッチ間で異なっていることを特徴とする請求項１，２，３，４，５又は６記載の遠心送風機。   The pitch of a large number of blades (16), (16)... Is unequal, and the rate of change of the curvature α of the curved portion of the side plate (15) is the pitch of the blades (16), (16). The centrifugal blower according to claim 1, wherein the centrifugal blower is different between the two. 多数枚の羽根（１６），（１６）・・・のピッチが不等ピッチであり、羽根（１１）全体の重心位置が回転軸上に重なるように側板（１５）の曲面形状が設定されていることを特徴とする請求項７記載の遠心送風機。   The curved shape of the side plate (15) is set so that the pitch of the multiple blades (16), (16)... Is unequal, and the center of gravity of the entire blade (11) overlaps the rotation axis. The centrifugal blower according to claim 7, wherein the centrifugal blower is provided. 空気調和機用室内機の送風機として構成されていることを特徴とする請求項１，２，３，４，５，６，７又は８記載の遠心送風機。   The centrifugal blower according to claim 1, 2, 3, 4, 5, 6, 7 or 8, wherein the centrifugal blower is configured as a blower of an indoor unit for an air conditioner.
JP2007067730A 2007-03-16 2007-03-16 Centrifugal blower Pending JP2008223741A (en)

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Cited By (8)

* Cited by examiner, † Cited by third party
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JP2010185456A (en) * 2009-02-12 2010-08-26 Ebm - Papst Mulfingen Gmbh & Co Kg Impeller for use in centrifugal blower or diagonal flow blower
JP2011080409A (en) * 2009-10-07 2011-04-21 Mitsubishi Electric Corp Centrifugal blower and electric vacuum cleaner
US8932019B2 (en) 2010-02-26 2015-01-13 Emb-Papst Mulfingen Gmbh & Co. Kg Radial or diagonal fan wheel
CN105275875A (en) * 2015-10-15 2016-01-27 珠海格力电器股份有限公司 Centrifugal fan blade and centrifugal fan
EP3048308A1 (en) * 2015-01-22 2016-07-27 LG Electronics Inc. Centrifugal fan
WO2019048241A1 (en) * 2017-09-06 2019-03-14 Ebm-Papst Mulfingen Gmbh & Co. Kg Covered radial fan wheel with a periodically and asymmetrically shaped plate
US20210372426A1 (en) * 2020-05-28 2021-12-02 Ebm-Papst Mulfingen Gmbh & Co. Kg Impeller With A Seamless Connection Of The Impeller Blades To A Disc Body
WO2023232660A1 (en) * 2022-05-31 2023-12-07 Ebm-Papst Mulfingen Gmbh & Co. Kg Cooling wheel for actively cooling a stator of an electric motor

Cited By (15)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2010185456A (en) * 2009-02-12 2010-08-26 Ebm - Papst Mulfingen Gmbh & Co Kg Impeller for use in centrifugal blower or diagonal flow blower
JP2011080409A (en) * 2009-10-07 2011-04-21 Mitsubishi Electric Corp Centrifugal blower and electric vacuum cleaner
KR101764430B1 (en) * 2010-02-26 2017-08-02 에베엠-펩스트 물핑겐 게엠베하 운트 코. 카게 Radial- or diagonal-fan impeller
US8932019B2 (en) 2010-02-26 2015-01-13 Emb-Papst Mulfingen Gmbh & Co. Kg Radial or diagonal fan wheel
US9989073B2 (en) 2015-01-22 2018-06-05 Lg Electronics Inc. Centrifugal fan
KR20160090617A (en) * 2015-01-22 2016-08-01 엘지전자 주식회사 Centrifugal Fan
CN105822572A (en) * 2015-01-22 2016-08-03 Lg电子株式会社 Centrifugal fan
KR101720491B1 (en) * 2015-01-22 2017-03-28 엘지전자 주식회사 Centrifugal Fan
EP3048308A1 (en) * 2015-01-22 2016-07-27 LG Electronics Inc. Centrifugal fan
CN105275875A (en) * 2015-10-15 2016-01-27 珠海格力电器股份有限公司 Centrifugal fan blade and centrifugal fan
WO2019048241A1 (en) * 2017-09-06 2019-03-14 Ebm-Papst Mulfingen Gmbh & Co. Kg Covered radial fan wheel with a periodically and asymmetrically shaped plate
US11143197B2 (en) 2017-09-06 2021-10-12 Ebm-Papst Mulfingen Gmbh & Co. Kg Covered radial fan wheel with a periodically and asymmetrically shaped plate
US20210372426A1 (en) * 2020-05-28 2021-12-02 Ebm-Papst Mulfingen Gmbh & Co. Kg Impeller With A Seamless Connection Of The Impeller Blades To A Disc Body
US11649829B2 (en) * 2020-05-28 2023-05-16 Ebm-Papst Mulfingen Gmbh & Co. Kg Impeller with a seamless connection of the impeller blades to a disc body
WO2023232660A1 (en) * 2022-05-31 2023-12-07 Ebm-Papst Mulfingen Gmbh & Co. Kg Cooling wheel for actively cooling a stator of an electric motor

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