WO2014167707A1 - Centrifugal fan - Google Patents
Centrifugal fan Download PDFInfo
- Publication number
- WO2014167707A1 WO2014167707A1 PCT/JP2013/061042 JP2013061042W WO2014167707A1 WO 2014167707 A1 WO2014167707 A1 WO 2014167707A1 JP 2013061042 W JP2013061042 W JP 2013061042W WO 2014167707 A1 WO2014167707 A1 WO 2014167707A1
- Authority
- WO
- WIPO (PCT)
- Prior art keywords
- impeller
- scroll casing
- air
- centrifugal blower
- drive motor
- Prior art date
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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
- F04D29/40—Casings; Connections of working fluid
- F04D29/42—Casings; Connections of working fluid for radial or helico-centrifugal pumps
- F04D29/4206—Casings; Connections of working fluid for radial or helico-centrifugal pumps especially adapted for elastic fluid pumps
- F04D29/4226—Fan casings
-
- 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
Definitions
- the present invention relates to the structure of a centrifugal fan provided with a scroll casing, particularly for ventilation and air conditioning.
- a centrifugal blower equipped with a scroll casing having a predetermined expansion ratio in the airflow direction in the air passage cross-sectional area collects the dynamic pressure of the air blown out from the impeller at the scroll casing and moves toward the air outlet.
- static pressure recovery is performed to convert dynamic pressure into static pressure. Therefore, the static pressure is highest in the vicinity of the blower outlet of the blower.
- the effect of recovering the static pressure by the scroll casing is small in a region where the air passage cross-sectional area is narrow with the tongue portion partitioning the blower outlet and the air passage in the blower as a boundary, the static pressure is low. That is, due to the configuration of the centrifugal blower, the largest internal pressure difference occurs at the tongue.
- the air flowing in the vicinity of the air outlet has a high static pressure, a part of the flow is not blown out from the air outlet, and a reverse flow is generated into the blower air passage having a low static pressure. In particular, it tends to flow backward from the blower air passage through the back side of the impeller main plate (the gap between the impeller and the scroll casing) toward the axial center of the drive motor having a weak flow. Similarly, the flow that collides with the tongue wall surface may enter the back side of the main plate of the impeller.
- the centrifugal blower as the prior art has a uniform flow between the impeller and the bottom wall of the scroll casing facing the impeller in the backflow of the impeller main plate.
- the direction of air inflow is not uniquely determined and is unstable.
- FIG. 12 shows, the flow which entered the main plate back side of the impeller easily flows out from the back side of the impeller to the air passage inside the blower again without passing through the opening of the main plate of the impeller. Become. Therefore, the direction in which the air flows out is not uniquely determined and becomes unstable.
- the position and size of the opening provided on the main plate of the impeller are devised by using the flow of air that enters the back side of the main plate of the impeller as described above.
- the improvement of the blower which made the flow of air around this drive motor and reduced the blowing noise while cooling the drive motor has been made (for example, see Patent Document 1).
- JP 2012-13035 A (refer to claim 1)
- the air flowing in the vicinity of the outlet has a high static pressure, so a part of the flow enters the back side of the main plate of the impeller.
- the impeller main plate can be back from any direction around the impeller. And air enters.
- the direction in which the air flows is not uniquely determined and becomes unstable, and the turbulence of the air flow and the pressure fluctuation increase, which may have adverse effects such as a decrease in blowing performance, an increase in noise, and occurrence of surging.
- the present invention has been made to solve such conventional problems, and rectifies the flow of air on the back side of the main plate of the impeller by using a simple and inexpensive means, and the turbulence and pressure of the airflow
- An object of the present invention is to provide a centrifugal blower that reduces fluctuations and improves the blowing noise performance. It is another object of the present invention to provide a centrifugal blower that facilitates the flow of air to the surface side (suction port side) of the impeller main plate and further enhances the cooling effect of the drive motor.
- a centrifugal blower is a centrifugal blower including a scroll casing, an impeller that is arranged in a ring shape with a plurality of blades arranged in an annular shape, and a drive motor that drives the impeller,
- the scroll casing bottom wall surface facing the impeller is provided with an annular bulging portion protruding toward the impeller side, and an airflow inflow portion through which an airflow flows is formed in a part of the bulging portion.
- air entering the back side of the main plate of the impeller is formed by forming an airflow inflow portion on the bottom wall surface of the scroll casing. Since the air flows uniquely and stably from the outlet side toward the axial center of the drive motor, it is possible to obtain a blower in which blowing noise is reduced and the cooling effect of the drive motor is further enhanced.
- FIG. 1 is a top view of a centrifugal blower according to Embodiment 1 of the present invention.
- FIG. 2 is a longitudinal sectional view (X1-'X1) of the centrifugal blower of FIG. 1 as seen from the direction intersecting the rotation axis.
- FIG. 3 is a cross-sectional view (Y-'Y) seen from the axial direction of the centrifugal fan of FIG.
- FIG. 4 is also a cross-sectional view (Z-'Z).
- FIG. 5 is a shape example of a baffle plate provided on the bottom wall surface of the scroll casing.
- FIG. 6 is a shape example of a guide plate provided on the bottom wall surface of the scroll casing.
- the centrifugal blower 1 includes a drive motor 2, an impeller 3, and a scroll casing 4.
- the impeller 3 includes a main plate 6 provided with a plurality of openings 5, a plurality of blades 7, and an annular member 8 for reinforcement.
- the scroll casing 4 includes a flow path having a predetermined expansion ratio in the airflow direction in the air passage cross-sectional area, and includes a suction port 9 on the upper surface, and an air outlet 10 and a tongue portion 11 on the side surface.
- the scroll casing 4 is provided with an annular bulging portion 4b projecting toward the impeller 3 on the scroll casing bottom wall surface 4a facing the impeller 3.
- the impeller 3 holds a predetermined gap with the bulging portion 4 b of the scroll casing 4 so that it can be rotated by the drive motor 2.
- a concave portion 12 through which air can flow is formed in the bulging portion 4 b on the outlet 10 side of the scroll casing 4. Therefore, the bulging portion 4b has a shape in which a part of the annular shape is cut off by the concave portion.
- the static pressure recovery effect by the scroll casing 4 is small in a region where the cross-sectional area of the air passage is narrow with the tongue portion 11 partitioning the air outlet 10 of the centrifugal blower 1 and the air passage in the air blower as a boundary, the static pressure is low. That is, due to the configuration of the centrifugal blower 1, the largest internal pressure difference occurs at the tongue 11.
- the air flowing in the vicinity of the air outlet 10 has a high static pressure, a part of the flow is not blown out from the air outlet 10 to the outside, and a reverse flow is generated in the blower air passage having a low static pressure.
- it flows backward from the blower air passage through the back surface 6a side of the main plate 6 of the impeller 3 (the gap between the impeller 3 and the bulging portion 4b of the scroll casing) toward the axial center of the drive motor 2 where the flow is weak. Is likely to occur.
- the flow that collides with the wall surface of the tongue portion 11 may enter the back surface 6a side of the main plate 6 of the impeller 3 in the same manner.
- the centrifugal blower 1 according to Embodiment 1 of the present invention is such that the expansion of the scroll casing bottom wall surface 4a is such that the gap between the back surface 6a of the main plate 6 of the impeller 3 and the bulging portion 4b of the scroll casing bottom wall surface 4a is locally expanded.
- a recessed portion 12 is provided in the protruding portion 4b. Therefore, the flow of air that tends to enter the back surface 6 a side (the gap between the impeller 3 and the scroll casing 4) of the impeller 3 is concentrated in the vicinity of the recess 12.
- the centrifugal blower 1 provided with the scroll casing 4 as described above has a high static pressure in the vicinity of the air outlet 10 due to its structure. Therefore, as shown in FIG. 4, by providing a recess 12 in the bulging portion 4 b of the scroll casing bottom wall surface 4 a in the vicinity of the outlet 10 of the centrifugal blower 1, the rear plate 6 a side of the main plate 6 of the impeller 3 is moved toward the rear surface 6 a side. The incoming flow is more likely to be concentrated near the recess 12.
- the concave portion 12 has a function of uniquely determining the air flow direction by serving as an inlet for the flow of air entering the back surface 6a of the impeller 3.
- the backflow of air entering the back surface 6a side of the main plate 6 of the impeller 3 is stably formed. Part of this flow flows from the outlet 10 toward the axial center of the drive motor 2 and eventually flows through the opening 5 of the main plate 6 to the surface 6b side of the main plate 6 of the impeller 3. A is formed.
- a baffle plate 13 that obstructs the flow of air entering the back surface 6a side of the main plate 6 of the impeller 3 except in the vicinity of the blowout port 10 may be provided upright.
- the baffle plate 13 is provided in a scroll casing bottom wall surface 4a facing the outer peripheral edge of the impeller 3 in an annular shape protruding toward the impeller 3 side. And since the baffle plate 13 is provided except the blower outlet 10 side, this opening part 5 plays the role of the inflow port which introduces the high static pressure air near the blower outlet 10 to the back surface 6a side of the impeller 3. Fulfill. Therefore, it has the function of uniquely determining the direction of air flow, like the recess 12 of the bulging portion 4b.
- the air that has entered the back surface 6 a side of the main plate 6 of the impeller 3 flows stably toward the axial center direction of the drive motor 2.
- the guide plate 14 may be provided on the scroll casing bottom wall surface 4a.
- the shape of the guide plate 14 may be any shape as long as the airflow can be guided toward the axial center of the drive motor 2, such as an arcuate standing portion shape as shown in FIG. Can also be selected.
- Embodiment 2 In the first embodiment, in the vicinity of the air outlet 10 of the centrifugal blower 1, the flow entering the back surface 6a side of the main plate 6 of the impeller 3 is concentrated in the vicinity of the concave portion 12, and the concave portion 12 is an air flow inlet. However, in the second embodiment, the outlet of the air flow that has entered the back surface 6a side of the main plate 6 of the impeller 3 has been shown. Is the configuration of the centrifugal blower 1 that uniquely determines the air flow direction. This will be described with reference to FIGS.
- FIG. 7 is a top view of the centrifugal blower according to Embodiment 2 of the present invention.
- FIG. 8 is a longitudinal sectional view (X2-'X2) of the centrifugal blower of FIG. 7 as seen from the direction intersecting the rotation axis.
- the centrifugal blower 1 according to the second embodiment has a bowl-like shape on the case wall surface 2 a of the drive motor 2, which is symmetric with respect to the rotation axis of the drive motor 2 with respect to the outlet 10.
- the rectifying guide 15 is provided.
- the rectifying guide 15 is not provided on the outlet 10 side of the scroll casing 4. That is, the rectifying guide 15 of the present embodiment is installed at a position corresponding to the bulging portion 4b and the baffle plate 13 in the first embodiment.
- the flow of air that has entered the back surface 6 a side of the main plate 6 of the impeller 3 passes through the periphery of the drive motor 2, and then is guided by the rectifying guide 15 and passes through the opening 5 of the main plate 6 of the impeller 3. It becomes easy to flow out to the surface 6b side of the impeller 3. That is, the rectifying guide 15 and the opening 5 of the main plate 6 stably serve as an outlet for the flow of air that has entered the back surface 6a side of the main plate 6 of the impeller 3 so that the direction of air flow is unique. Has a function to be determined.
- the outflow direction of the air that has entered the back surface 6a side of the main plate 6 of the impeller 3 can be stabilized, so the axial center of the drive motor 2 from the vicinity of the outlet 10
- the air flow toward the direction can be uniquely determined.
- the air that has entered the back surface 6 a side of the main plate 6 of the impeller 3 flows out to the surface 6 a side of the impeller 3 through the opening 5 of the main plate 6 of the impeller 3.
- This facilitates the flow of air around the drive motor 2. That is, the cooling effect of the drive motor 2 can be further enhanced by forming an air path through which air flows around the drive motor 2.
- the rectifying guide is provided on the case wall surface 2a of the drive motor 2 on the side symmetrical to the rotation axis of the drive motor 2 with respect to the outlet 10.
- a cooling fin having 15 may be attached.
- both the air flow adjusting means of the first embodiment and the second embodiment described above correspond to the shape change of only a specific part of the blower instead of the whole blower according to the internal pressure difference of the blower, the performance of the blower is improved. Is efficient. Moreover, an inexpensive drive motor can be used by further enhancing the cooling effect of the drive motor. Or a cheaper blower can be realized by minimizing the number of cooling fins.
- FIG. 9 is a graph comparing the air blowing characteristics of the centrifugal fan according to the embodiment of the present invention and the conventional centrifugal fan.
- a broken line is a blowing characteristic of a centrifugal fan having a conventional shape.
- a thin solid line is a blowing characteristic of a centrifugal blower that employs a configuration in which the flow entering the back surface 6a side of the main plate 6 of the impeller 3 of the first embodiment is concentrated in the airflow inflow portion.
- the thick solid line represents the flow of air that has entered the back surface 6a side of the main plate 6 of the impeller 3 in the configuration of the first embodiment and the flow guide 15 and the opening 5 of the main plate 6 of the second embodiment.
- the blowing characteristics of the solid blower 1 and the centrifugal blower 1 having both the first and second embodiments are more solid than the conventional centrifugal blower having a broken line in almost the entire region. It can be seen that it has improved.
- FIG. 10 is a graph comparing the noise characteristics of the centrifugal fan 1 according to the embodiment of the present invention and a conventional centrifugal fan.
- the noise characteristics of the solid blower according to the first embodiment and the centrifugal fan having the shapes adopting both the first and second embodiments are improved as compared with the conventional blower of FIG. I understand that.
- a noise reduction effect of about ⁇ 1.5 dB was obtained in comparison with the same air volume.
- air that has entered the back surface 6a side of the main plate 6 of the impeller 3 by combining either or both of the airflow adjusting means of the first and second embodiments described above is impeller 3.
- a circulation flow A is formed which flows through the opening 5 of the main plate 6 and flows toward the surface 6 b of the main plate 6 of the impeller 3. Therefore, the turbulence noise performance can be improved by reducing the turbulence of air flow and pressure fluctuation on the back surface 6a side of the main plate 6 of the impeller 3. Further, air can easily flow out to the surface 6 a side (suction port side) of the main plate 6 of the impeller 3, and a centrifugal blower that further enhances the cooling effect of the drive motor 2 can be obtained.
- the present invention is applied to the centrifugal fan provided with the scroll casing.
- the present invention is not limited to this, and can be applied to a multi-blade fan using a multi-blade impeller.
- the present invention is applied to a blower for ventilation and air conditioning.
- the present invention is not limited to this and can be applied to other devices.
Abstract
Description
図1は、本発明の実施の形態1に係る遠心送風機の上面図である。
図2は、図1の遠心送風機を回転軸と交差する方向からみた縦断面図(X1-‘X1)である。
図3は、図2の遠心送風機の軸方向から見た横断面図(Y-‘Y)である。
図4は、同様に横断面図(Z-‘Z)である。
図5は、スクロールケーシング底壁面に設ける邪魔板の形状例である。
図6は、スクロールケーシング底壁面に設ける案内板の形状例である。
FIG. 1 is a top view of a centrifugal blower according to
FIG. 2 is a longitudinal sectional view (X1-'X1) of the centrifugal blower of FIG. 1 as seen from the direction intersecting the rotation axis.
FIG. 3 is a cross-sectional view (Y-'Y) seen from the axial direction of the centrifugal fan of FIG.
FIG. 4 is also a cross-sectional view (Z-'Z).
FIG. 5 is a shape example of a baffle plate provided on the bottom wall surface of the scroll casing.
FIG. 6 is a shape example of a guide plate provided on the bottom wall surface of the scroll casing.
上記実施の形態1においては、遠心送風機1の吹出口10の近傍において、羽根車3の主板6の背面6a側へと入り込む流れを凹部12付近に集約し、凹部12は空気の流れの流入口の役割を果たすことで、空気の流れる方向を一意的に定めた例を示したが、本実施の形態2では、羽根車3の主板6の背面6a側へと入り込んだ空気の流れの流出口を確保することで、空気の流れる方向を一意的に定める遠心送風機1の構成である。図7、8に基づいて説明する。
In the first embodiment, in the vicinity of the
図8は、図7の遠心送風機を回転軸と交差する方向からみた縦断面図(X2-‘X2)である。
図7および図8に示されるように、本実施の形態2の遠心送風機1は、吹出口10に対して駆動モータ2の回転軸と対称側となる駆動モータ2のケース壁面2aに、鍔状の整流ガイド15を備えている。この整流ガイド15は、スクロールケーシング4の吹出口10側には設けられていない。すなわち、本実施の形態の整流ガイド15は、実施の形態1における膨出部4bや邪魔板13に対応する位置に設置されている。 FIG. 7 is a top view of the centrifugal blower according to
FIG. 8 is a longitudinal sectional view (X2-'X2) of the centrifugal blower of FIG. 7 as seen from the direction intersecting the rotation axis.
As shown in FIGS. 7 and 8, the
本発明の最良の形態である実施の形態1と2の双方を採用した形状の遠心送風機1を実施した場合、同一風量時比較において約-1.5dBの騒音低減効果が得られた。 FIG. 10 is a graph comparing the noise characteristics of the
When the
Claims (8)
- スクロールケーシングと、複数の翼を環状に配列し前記スクロールケーシング内に収容される羽根車と、前記羽根車を駆動する駆動モータと、を備える遠心送風機であって、
前記羽根車に対向する前記スクロールケーシング底壁面には前記羽根車側に突出する環状の膨出部が設けられ、前記膨出部の一部に気流が流通する気流流入部を形成したことを特徴とする遠心送風機。 A centrifugal blower comprising: a scroll casing; an impeller that is arranged in a ring shape with a plurality of blades accommodated in the scroll casing; and a drive motor that drives the impeller,
The scroll casing bottom wall surface facing the impeller is provided with an annular bulging portion protruding toward the impeller side, and an airflow inflow portion through which an airflow flows is formed in a part of the bulging portion. And centrifugal blower. - 前記気流流入部は、前記膨出部に設けられた凹部であることを特徴とする請求項1に記載の遠心送風機。 The centrifugal air blower according to claim 1, wherein the airflow inflow portion is a recess provided in the bulging portion.
- 前記凹部は、前記スクロールケーシングの吹出口側に設けられたことを特徴とする請求項2に記載の遠心送風機。 The centrifugal blower according to claim 2, wherein the concave portion is provided on an outlet side of the scroll casing.
- 前記凹部は、前記スクロールケーシングの舌部側に設けられたことを特徴とする請求項2または3に記載の遠心送風機。 The centrifugal blower according to claim 2 or 3, wherein the concave portion is provided on a tongue side of the scroll casing.
- 前記駆動モータはケースを備えており、前記ケースのケース壁面には気流を案内する整流ガイドを設けたことを特徴とする請求項1~4のいずれか一項に記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 4, wherein the drive motor includes a case, and a rectifying guide for guiding an airflow is provided on a case wall surface of the case.
- 前記整流ガイドは、前記スクロールケーシングの吹出口に対して前記駆動モータの回転軸と対称側となる前記ケース壁面に配置されたことを特徴とする請求項5に記載の遠心送風機。 6. The centrifugal blower according to claim 5, wherein the rectifying guide is disposed on the case wall surface that is symmetrical to the rotational axis of the drive motor with respect to the outlet of the scroll casing.
- 前記整流ガイドは、前記スクロールケーシング底壁面に設けられた前記気流流入部を除いた部分に対応して配置されたことを特徴とする請求項5または6に記載の遠心送風機。 The centrifugal air blower according to claim 5 or 6, wherein the rectifying guide is disposed corresponding to a portion excluding the air flow inflow portion provided on the bottom wall surface of the scroll casing.
- 前記気流流入部には、前記スクロールケーシング底壁面に気流を案内する案内板を設けたことを特徴とする請求項1~7のいずれか一項に記載の遠心送風機。 The centrifugal blower according to any one of claims 1 to 7, wherein a guide plate for guiding the airflow is provided on the bottom wall surface of the scroll casing at the airflow inflow portion.
Priority Applications (3)
Application Number | Priority Date | Filing Date | Title |
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JP2015511047A JP6058125B2 (en) | 2013-04-12 | 2013-04-12 | Centrifugal blower |
PCT/JP2013/061042 WO2014167707A1 (en) | 2013-04-12 | 2013-04-12 | Centrifugal fan |
CN201390001162.6U CN205089681U (en) | 2013-04-12 | 2013-04-12 | Centrifugal blower |
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PCT/JP2013/061042 WO2014167707A1 (en) | 2013-04-12 | 2013-04-12 | Centrifugal fan |
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CN (1) | CN205089681U (en) |
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Cited By (1)
Publication number | Priority date | Publication date | Assignee | Title |
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EP3919747A4 (en) * | 2019-02-20 | 2022-04-06 | Huawei Technologies Co., Ltd. | Centrifugal fan and terminal |
Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5928700U (en) * | 1982-08-19 | 1984-02-22 | 三菱重工業株式会社 | centrifugal blower |
JPS63128292U (en) * | 1987-02-16 | 1988-08-22 | ||
JPH0532798U (en) * | 1991-10-14 | 1993-04-30 | 三菱重工業株式会社 | Blower |
JP2006283678A (en) * | 2005-04-01 | 2006-10-19 | Japan Servo Co Ltd | Centrifugal fan |
JP2012013090A (en) * | 2011-08-31 | 2012-01-19 | Daikin Industries Ltd | Air blowing device |
-
2013
- 2013-04-12 WO PCT/JP2013/061042 patent/WO2014167707A1/en active Application Filing
- 2013-04-12 JP JP2015511047A patent/JP6058125B2/en active Active
- 2013-04-12 CN CN201390001162.6U patent/CN205089681U/en not_active Expired - Fee Related
Patent Citations (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
JPS5928700U (en) * | 1982-08-19 | 1984-02-22 | 三菱重工業株式会社 | centrifugal blower |
JPS63128292U (en) * | 1987-02-16 | 1988-08-22 | ||
JPH0532798U (en) * | 1991-10-14 | 1993-04-30 | 三菱重工業株式会社 | Blower |
JP2006283678A (en) * | 2005-04-01 | 2006-10-19 | Japan Servo Co Ltd | Centrifugal fan |
JP2012013090A (en) * | 2011-08-31 | 2012-01-19 | Daikin Industries Ltd | Air blowing device |
Cited By (2)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
EP3919747A4 (en) * | 2019-02-20 | 2022-04-06 | Huawei Technologies Co., Ltd. | Centrifugal fan and terminal |
US11719256B2 (en) | 2019-02-20 | 2023-08-08 | Huawei Technologies Co., Ltd. | Centrifugal fan and terminal |
Also Published As
Publication number | Publication date |
---|---|
JP6058125B2 (en) | 2017-01-11 |
CN205089681U (en) | 2016-03-16 |
JPWO2014167707A1 (en) | 2017-02-16 |
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