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WO2018138808A1 - Soufflante centrifuge - Google Patents

Soufflante centrifuge Download PDF

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Publication number
WO2018138808A1
WO2018138808A1 PCT/JP2017/002584 JP2017002584W WO2018138808A1 WO 2018138808 A1 WO2018138808 A1 WO 2018138808A1 JP 2017002584 W JP2017002584 W JP 2017002584W WO 2018138808 A1 WO2018138808 A1 WO 2018138808A1
Authority
WO
WIPO (PCT)
Prior art keywords
impeller
centrifugal blower
guide plate
scroll casing
reinforcing ring
Prior art date
Application number
PCT/JP2017/002584
Other languages
English (en)
Japanese (ja)
Inventor
一輝 岡本
健太 桶谷
悠太 戸田
健一 迫田
Original Assignee
三菱電機株式会社
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by 三菱電機株式会社 filed Critical 三菱電機株式会社
Priority to PCT/JP2017/002584 priority Critical patent/WO2018138808A1/fr
Priority to JP2018563994A priority patent/JP6771589B2/ja
Publication of WO2018138808A1 publication Critical patent/WO2018138808A1/fr

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Classifications

    • 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
    • F04D29/08—Sealings
    • F04D29/16—Sealings between pressure and suction sides
    • F04D29/161—Sealings between pressure and suction sides especially adapted for elastic fluid pumps
    • F04D29/162—Sealings between pressure and suction sides especially adapted for elastic fluid pumps of a centrifugal flow wheel
    • 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

Definitions

  • the present invention relates to a centrifugal blower provided with a scroll casing.
  • the centrifugal blower has a structure that blows out the sucked air in the centrifugal direction of the rotating shaft, and inertia force acts on the suction flow. Therefore, the airflow blown into the scroll casing through the impeller forms a velocity distribution biased toward the main plate side of the impeller. Part of the airflow blown out from the impeller into the scroll casing forms a flow that winds up from the main plate side of the impeller toward the blade tip along the inner wall surface of the scroll casing, and reaches the vicinity of the blade tip of the impeller. It becomes a circulating flow to reach. Such a circulating flow not only causes a loss of ventilation, but also becomes a source of noise when the circulating flow collides with the blades of the impeller.
  • the scroll casing of the centrifugal blower has an enlargement ratio, and when the air blown out from the impeller is collected by the scroll casing, the air passage cross-sectional area is gradually enlarged toward the outlet, Dynamic pressure is converted to static pressure. Therefore, static pressure becomes high near the blower outlet of the centrifugal blower.
  • the static pressure in the air passage in the centrifugal blower becomes lower at the tongue portion that partitions the blower outlet of the centrifugal blower and the air passage in the blower. That is, due to the configuration of the centrifugal blower, the internal pressure difference becomes the largest at the tongue. The above-described pressure change with the tongue as a boundary disturbs the airflow in the centrifugal blower, which causes a reduction in blowing performance and noise.
  • the centrifugal blower disclosed in Patent Document 1 improves the air blowing efficiency by providing a strip-shaped blade on the suction side plate of the impeller to reduce air leaking from the gap between the bell mouth and the side plate of the impeller. I let you. Moreover, the airflow was increased by sending the air which was going to circulate out of a scroll casing using the rotational force of an impeller.
  • the present invention has been made in view of the above, and an object thereof is to obtain a centrifugal blower that achieves both improvement in blowing performance and reduction in noise.
  • the present invention includes a scroll casing, a drive motor, a main plate that rotates around a shaft of the drive motor, and a plurality of main wings arranged in an annular shape on the main plate,
  • a centrifugal blower including a reinforcing ring attached to an outer peripheral portion of a main wing and extending in a direction away from the shaft, and having an impeller housed in a scroll casing.
  • the impeller has a guide plate that is arranged in a reinforcing ring and that sends out air from the inner peripheral side of the impeller to the outer peripheral side.
  • the centrifugal blower according to the present invention has an effect that it is possible to achieve both improvement in blowing performance and reduction in noise.
  • FIG. 1 is a perspective view of a centrifugal blower according to Embodiment 1.
  • FIG. 1 which shows the example of a shape of the reinforcement ring and guide plate of the centrifugal blower which concern on Embodiment 1.
  • FIG. 1 is a perspective view of a centrifugal blower according to Embodiment 1.
  • FIG. which shows the example of a shape of the reinforcement ring and guide plate of the centrifugal blower which concern on Embodiment
  • FIG. 1 The figure which shows the ventilation characteristic of the centrifugal blower which concerns on Embodiment 1,2.
  • FIG. 1 is a top view of a centrifugal blower according to Embodiment 1 of the present invention.
  • FIG. 2 is a cross-sectional view of the centrifugal blower according to Embodiment 1, and shows a cross section taken along line II-II in FIG.
  • FIG. 3 is a cross-sectional view of the centrifugal blower according to Embodiment 1, and shows a cross section taken along line III-III in FIG.
  • FIG. 4 is a perspective view of the centrifugal blower according to the first embodiment.
  • the centrifugal blower 1 includes a drive motor 2 that is a power source, an impeller 3 installed on a shaft 2 a of the drive motor 2, and a scroll casing 4 that collects an airflow blown from the impeller 3.
  • the impeller 3 includes a disk-shaped main plate 5, a plurality of main wings 6 arranged in an annular shape on the main plate 5 at intervals, and an annular reinforcing ring 7 attached to the outer periphery of the main wing 6.
  • An arcuate guide plate 8 arranged in an annular shape is attached to the reinforcing ring 7.
  • the guide plate 8 is an arcuate blade.
  • the impeller 3 has an outer diameter at the guide plate 8 portion larger than an outer diameter at the main wing 6 portion. Further, the impeller 3 has an outer diameter at the reinforcing ring 7 that is equal to or larger than an outer diameter at the guide plate 8.
  • the scroll casing 4 includes a suction port 10 that takes in air, a bell mouth 9 that rectifies the air that is taken in from the suction port 10, a blower outlet 11 that is an outlet of an airflow blown from the impeller 3, a blower outlet 11, and a scroll casing. 4 is provided with a tongue portion 12 for partitioning the air passage in 4.
  • the centrifugal blower 1 blows out the air sucked from the suction port 10 into the scroll casing 4 through the impeller 3. Since an inertial force acts on the suction flow, the air flow in the scroll casing 4 forms a faster velocity distribution as it approaches the main plate 5 of the impeller 3.
  • Part of the airflow blown out from the impeller 3 into the scroll casing 4 forms a flow that winds from the main plate 5 side of the impeller 3 toward the blade tip along the inner wall surface 4 a of the scroll casing 4. It becomes a circulating flow that reaches around the tip of No.3.
  • FIG. 5 is a diagram schematically showing the air flow of the centrifugal blower according to the first embodiment, and shows the air flow at the V portion in FIG.
  • a part of the circulating flow X that has reached the vicinity of the blade tip of the impeller 3 is taken in by the reinforcing ring 7 and the guide plate 8, and an airflow Y that is sent from the inner peripheral side toward the outer peripheral side is formed.
  • the reinforcing ring 7 extends in a direction perpendicular to the shaft 2 a that is the rotation axis of the impeller 3.
  • the air flow F blown into the scroll casing 4 through the main wing 6 of the impeller 3 from the suction port 10 of the centrifugal blower 1 and the guide plate 8 of the reinforcing ring 7 are sent from the inner peripheral side to the outer peripheral side.
  • the collision of the generated airflow Y in the scroll casing 4 is suppressed by the reinforcing ring 7 being a partition plate. Therefore, the airflow is less likely to be disturbed in the scroll casing 4, and the air blowing performance of the centrifugal fan 1 can be improved without deteriorating noise.
  • the reinforcing ring 7 is attached so that the upper surface 8a of the guide plate 8 is closer to the main plate 5 as shown in FIG. Therefore, the distance between the main plate 5 and the upper surface 6 a of the guide plate 8 in the axial direction of the shaft 2 a is less than the distance between the main plate 5 and the upper surface 6 a of the main wing 6.
  • the reinforcing ring 7 may be attached so that the upper surface 8a of the guide plate 8 is at the same position as the upper surface 6a of the main wing 6 of the impeller 3 in the rotation axis direction.
  • the reinforcing ring 7 so that the upper surface 8a of the guide plate 8 and the upper surface 6a of the main wing 6 of the impeller 3 are located on the same plane in the rotation axis direction, or the upper surface 8a of the guide plate 8 is closer to the main plate 5 side. Is attached, the circulating flow X reaching the periphery of the blade tip of the impeller 3 is not obstructed by the guide plate 8 and forms an arc from the bell mouth 9 side of the scroll casing 4 to the blade tip side of the impeller 3. Flowing into. Therefore, when the airflow Y is sent out from the inner peripheral side toward the outer peripheral side by the guide plate 8, less turbulence in the flow is required, and suppression of noise deterioration can be expected.
  • FIG. 6 and 7 are diagrams showing examples of shapes of the reinforcing ring and the guide plate of the centrifugal blower according to the first embodiment.
  • the direction in which the guide plate 8 is attached is made different from that of the main wing 6, and the size of the guide plate 8 is changed as shown in FIG. May be. Since the direction of the guide plate 8 is opposite to that of the main wing 6 as shown in FIG. 6, the pressure of the airflow Y sent from the inner peripheral side toward the outer peripheral side by the guide plate 8 can be increased. Even when the airflow of the circulating flow X reaching the periphery of the blade tip is large, the airflow Y is easily sent out.
  • the guide plate 8 is an arcuate blade.
  • the guide plate 8 is not limited to this, and may be a flat plate that can be formed at a lower cost. Further, the guide plate 8 may be formed using a sound absorbing material in order to reduce noise.
  • the reinforcing ring 7 provided on the impeller 3 is extended in a direction orthogonal to the shaft 2a within a range in which the impeller 3 can rotate within the scroll casing 4. Accordingly, the reinforcing ring 7 can be added with a role of a rectifying plate that suppresses the occurrence of turbulence in the air flow in the scroll casing 4 due to a rapid pressure change with the tongue 12 as a boundary. As a result, the blowout flow of the centrifugal blower 1 is made uniform gently, and noise can be reduced while improving the blowing performance.
  • the centrifugal blower 1 is provided with a plurality of guide plates 8 on the reinforcing ring 7.
  • the guide plate 8 captures a part of the circulating flow reaching the periphery of the blade tip of the impeller 3, while the flow of air sent out from the guide plate 8 and the main wing 6 of the impeller 3 are reduced.
  • the reinforcing ring 7 can prevent the air flow that has passed through and blown into the scroll casing 4 from colliding with the scroll casing 4. Therefore, the airflow is less likely to be disturbed in the scroll casing 4, and the air blowing performance of the centrifugal fan 1 can be improved without deteriorating noise.
  • the guide plate 8 is installed on the reinforcing ring 7, so that the installation location and size of the guide plate 8 are loosely limited, and the guide plate 8 has a size that satisfies the blowing performance. It is easy to install.
  • FIG. FIG. 8 is a cross-sectional view of the centrifugal blower according to Embodiment 2 of the present invention, and shows a cross section corresponding to the line II-II in FIG.
  • FIG. 9 is a cross-sectional view of the centrifugal fan according to the second embodiment, showing a cross section taken along line IX-IX in FIG.
  • the centrifugal blower 101 according to the second embodiment is provided with a recess 13 on the inner wall surface of the tongue 12.
  • the reinforcing ring 7 can rotate without interfering with the tongue 12 by passing through the recess 13. Other than this, it is the same as the centrifugal blower 1 according to the first embodiment.
  • the scroll casing 4 The flow of air blown into the scroll casing 4 through the main wing 6 of the impeller 3 and the flow of air sent from the inner peripheral side to the outer peripheral side by the guide plate 8 of the reinforcing ring 7 are the scroll casing 4. In order to suppress a collision inside, it is better that the radial dimension of the reinforcing ring 7 is longer. In the centrifugal blower 101 according to the second embodiment, the dimension in the radial direction of the reinforcing ring 7 is a length that interferes with the tongue 12 if there is no recess 13.
  • the function of the reinforcing ring 7 of the impeller 3 to partition the flow in the scroll casing 4 is higher than that of the centrifugal blower 1 according to the first embodiment.
  • the guide plate 8 attached to the reinforcing ring 7 has a higher degree of freedom in designing the size, position and shape of the blades. Therefore, the circulating flow X reaching the periphery of the blade tip of the impeller 3 is efficiently taken in and guided.
  • the plate 8 facilitates sending air from the inner peripheral side toward the outer peripheral side.
  • the centrifugal blower 101 has a scroll with the tongue 12 as a boundary by extending the reinforcement ring 7 in the direction orthogonal to the rotation axis within a range in which the impeller 3 can rotate within the scroll casing 4.
  • the reinforcing ring 7 is added with a role of a rectifying plate that suppresses the turbulence of the flow in the scroll casing 4 due to a sudden pressure change in the casing 4. Since the reinforcing ring 7 serves as a current plate, the blowout flow of the centrifugal blower 101 is made uniform, and noise can be reduced while improving the blowing performance.
  • FIG. 10 is a diagram showing the air blowing characteristics of the centrifugal blower according to the first and second embodiments.
  • FIG. 11 is a diagram illustrating noise characteristics of the centrifugal blower according to the first and second embodiments.
  • the black circle plot indicates the fan efficiency ⁇ of the centrifugal blower 1 according to the first embodiment
  • the black square plot indicates the fan efficiency ⁇ of the centrifugal blower 101 according to the second embodiment.
  • the white circle plots indicate the fan efficiency ⁇ of the centrifugal blower according to the comparative example in which the guide plate 8 is not provided on the reinforcing ring 7.
  • FIG. 10 is a diagram showing the air blowing characteristics of the centrifugal blower according to the first and second embodiments.
  • FIG. 11 is a diagram illustrating noise characteristics of the centrifugal blower according to the first and second embodiments.
  • the black circle plot indicates the fan efficiency ⁇ of the centrifugal blower 1 according to the first embodiment
  • the black square plot indicates the
  • the black circle plot shows the specific noise K of the centrifugal fan 1 according to the first embodiment
  • the black square plot shows the specific noise K of the centrifugal blower 101 according to the second embodiment
  • the white circle plot shows the specific noise K of the centrifugal blower according to the comparative example in which the guide plate 8 is not provided on the reinforcing ring 7.
  • the fan efficiency ⁇ was calculated by the following formula (1)
  • the specific noise K was calculated by the following formula (2).
  • the centrifugal blower 1 according to the first embodiment and the centrifugal blower 101 according to the second embodiment are compared with the centrifugal blower according to the comparative example, without reducing the blowing performance.
  • a maximum characteristic of +2 pt in fan efficiency ⁇ and ⁇ 1.0 dB in specific noise K is obtained.
  • a multi-blade fan using a multi-blade impeller has been described as an example, but the present invention is not limited to a multi-blade fan, and can be applied to any centrifugal fan including a scroll casing. .
  • the single suction centrifugal blower is taken as an example, but the present invention is not limited to the single suction centrifugal blower, and can be applied to a double suction centrifugal blower.
  • centrifugal blower for ventilation air conditioning is given as an example.
  • the present invention can be applied to a centrifugal blower other than the ventilation air conditioning.
  • the configuration described in the above embodiment shows an example of the contents of the present invention, and can be combined with another known technique, and can be combined with other configurations without departing from the gist of the present invention. It is also possible to omit or change the part.

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Structures Of Non-Positive Displacement Pumps (AREA)

Abstract

La présente invention concerne une soufflante centrifuge (1) comportant: un carter (4) à volute; un moteur (2) d'entraînement; et un rouet (3) muni d'une plaque principale (5) qui tourne autour de l'arbre (2a) du moteur (2) d'entraînement, une pluralité de pales principales (6) qui sont disposées de façon annulaire sur la plaque principale (5), et un anneau (7) de renfort qui est fixé à la périphérie extérieure des pales principales (6) et qui s'étend dans la direction s'éloignant de l'arbre (2a), le rouet (3) étant contenu dans le carter (4) à volute. Le rouet (3) est doté de plaques (8) de guidage disposées sur l'anneau (7) de renfort et amenant de l'air du côté périphérique intérieur au côté périphérique extérieur du rouet (3).
PCT/JP2017/002584 2017-01-25 2017-01-25 Soufflante centrifuge WO2018138808A1 (fr)

Priority Applications (2)

Application Number Priority Date Filing Date Title
PCT/JP2017/002584 WO2018138808A1 (fr) 2017-01-25 2017-01-25 Soufflante centrifuge
JP2018563994A JP6771589B2 (ja) 2017-01-25 2017-01-25 遠心送風機

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
PCT/JP2017/002584 WO2018138808A1 (fr) 2017-01-25 2017-01-25 Soufflante centrifuge

Publications (1)

Publication Number Publication Date
WO2018138808A1 true WO2018138808A1 (fr) 2018-08-02

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ID=62978200

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PCT/JP2017/002584 WO2018138808A1 (fr) 2017-01-25 2017-01-25 Soufflante centrifuge

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JP (1) JP6771589B2 (fr)
WO (1) WO2018138808A1 (fr)

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05332293A (ja) * 1992-06-03 1993-12-14 Nippondenso Co Ltd 多翼送風機
WO1998053211A1 (fr) * 1997-05-21 1998-11-26 Toto Ltd. Soufflante centrifuge multi-pales
JP2011052626A (ja) * 2009-09-03 2011-03-17 Mitsubishi Heavy Ind Ltd 多翼遠心ファンおよびそれを用いた空気調和機

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05332293A (ja) * 1992-06-03 1993-12-14 Nippondenso Co Ltd 多翼送風機
WO1998053211A1 (fr) * 1997-05-21 1998-11-26 Toto Ltd. Soufflante centrifuge multi-pales
JP2011052626A (ja) * 2009-09-03 2011-03-17 Mitsubishi Heavy Ind Ltd 多翼遠心ファンおよびそれを用いた空気調和機

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JP6771589B2 (ja) 2020-10-21
JPWO2018138808A1 (ja) 2019-06-27

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