JP2010112285A - Centrifugal multiblade blower - Google Patents

Centrifugal multiblade blower Download PDF

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JP2010112285A
JP2010112285A JP2008286271A JP2008286271A JP2010112285A JP 2010112285 A JP2010112285 A JP 2010112285A JP 2008286271 A JP2008286271 A JP 2008286271A JP 2008286271 A JP2008286271 A JP 2008286271A JP 2010112285 A JP2010112285 A JP 2010112285A
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centrifugal multiblade
air
opening
multiblade fan
diameter
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JP5164801B2 (en
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Masatoshi Kawasaki
真俊 川埼
Tadashi Uchida
正 内田
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Sanden Corp
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Sanden Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To provide a centrifugal multiblade blower effectively reducing noise and maintaining blowing performance to a high level substantially the same as in the related art. <P>SOLUTION: This centrifugal multiblade blower includes a centrifugal multiblade fan having a plurality of blades around a rotary shaft, and a scroll casing in which the centrifugal multiblade fan is stored, and takes in air taken in from an air intake port opened in the scroll casing from the radially inner side between blades, and discharging the air to the radially outer side. A sound-deadening member abutted on the periphery of the air intake port and having an opening part opened in the intake air flow upstream direction is installed on the opening end outer side of the air intake port opened in the scroll casing. In the opening part of the sound-deadening member, the bore at an intake air flow upstream side end is larger than the bore of the air intake port, and the bore at the abutted part to the periphery of the air intake port is larger than the bore at the intake air flow upstream side end. <P>COPYRIGHT: (C)2010,JPO&INPIT

Description

本発明は、遠心式多翼送風機に関し、とくに、騒音を効果的に低減でき、且つ、送風性能が従来技術とほぼ同様の高い水準に維持された遠心式多翼送風機に関する。   The present invention relates to a centrifugal multiblade blower, and more particularly, to a centrifugal multiblade blower that can effectively reduce noise and has a blowing performance maintained at a high level that is substantially the same as that of the prior art.

従来より、遠心式多翼送風機において、ファン回転時の騒音を低減する方法が各種提案されている。例えば、特許文献１には、吸入口と同一内径を有する円筒形の騒音低減部材を吸入口に設けることにより、騒音の低減を実現したスクロール型遠心送風機が開示されている。
実開昭５９−１７５６９８号公報 Conventionally, various methods for reducing noise during fan rotation have been proposed for centrifugal multiblade fans. For example, Patent Document 1 discloses a scroll centrifugal blower that achieves noise reduction by providing a cylindrical noise reduction member having the same inner diameter as the suction port at the suction port.
Japanese Utility Model Publication No.59-175698

しかしながら、特許文献１に開示された方法においては、騒音低減部材の内径が吸入口と同一の大きさであるため、吸入口外縁部より径方向内側に向かって吸入される吸入空気流が騒音低減部材によって大きく阻害されてしまい、吸入空気量が減少し、遠心送風機の送風性能が低下するおそれがある。また、騒音低減部材が円筒形であることから、遠心ファンの回転による騒音が騒音低減部材の内周面に反射されて遠心送風機外へ漏れてしまい、騒音の効果的な低減が難しくなるという懸念もある。   However, in the method disclosed in Patent Document 1, since the inner diameter of the noise reduction member is the same size as the suction port, the intake air flow sucked radially inward from the outer edge of the suction port reduces noise. There is a risk that the member will be greatly obstructed, the amount of intake air will be reduced, and the blowing performance of the centrifugal blower will be reduced. In addition, since the noise reduction member is cylindrical, noise due to the rotation of the centrifugal fan is reflected on the inner peripheral surface of the noise reduction member and leaks out of the centrifugal fan, making it difficult to effectively reduce noise. There is also.

そこで本発明の課題は、騒音を効果的に低減でき、且つ、送風性能が従来技術とほぼ同様の高い水準に維持可能な遠心式多翼送風機を提供することにある。   SUMMARY OF THE INVENTION An object of the present invention is to provide a centrifugal multiblade fan that can effectively reduce noise and can maintain a blowing performance at a high level that is substantially the same as that of the prior art.

上記課題を解決するために、本発明に係る遠心式多翼送風機は、回転軸周りに複数のブレードを有する遠心式多翼ファンと、該遠心式多翼ファンが収納されるスクロールケーシングを有し、該スクロールケーシングに開口された空気吸入口から吸い込まれた空気を前記ブレード間における径方向内側から吸入し径方向外側に吐出する遠心式多翼送風機において、前記スクロールケーシングに開口された空気吸入口の開口端外側に、該空気吸入口の周囲に当接し吸入空気流上流方向へ開口する開口部を有する消音部材が付設されており、該消音部材の開口部においては、吸入空気流上流側端部における口径が前記空気吸入口の口径よりも大きく、前記空気吸入口の周囲への当接部における口径が前記吸入空気流上流側端部における口径よりも大きいことを特徴とするものからなる。   In order to solve the above problems, a centrifugal multiblade fan according to the present invention includes a centrifugal multiblade fan having a plurality of blades around a rotation axis, and a scroll casing in which the centrifugal multiblade fan is accommodated. In a centrifugal multiblade fan that sucks air sucked from an air suction port opened in the scroll casing from the radially inner side between the blades and discharges it radially outward, the air suction port opened in the scroll casing A silencer member having an opening that contacts the periphery of the air inlet and opens in the upstream direction of the intake airflow is attached to the outside of the opening end of the intake airflow. The diameter of the air intake port is larger than the diameter of the air intake port, and the diameter of the contact portion around the air intake port is larger than the diameter of the intake air flow upstream end. Ikoto consists those characterized by.

このような構成においては、空気吸入口の開口端外側に消音部材が付設されているので、空気吸入時において遠心式多翼ファンから発生する騒音の一部が、消音部材により空気吸入口内側方向へ反射されるが、消音部材の開口部の口径は、空気吸入口の周囲への当接部においては上記吸入空気流上流側端部の口径よりも大きいので、消音部材の騒音反射面はテーパ状になって空気吸入口の装置内部側に向くことになり、空気吸入口の外部へ放出される騒音の低減が効率よく達成される。また、消音部材の開口部の口径は、吸入空気流上流側端部においては空気吸入口の口径よりも大きいので、消音部材の内面は全範囲にわたって空気吸入口よりも大口径となるから、吸入空気流が消音部材により阻害されることはほとんどなく、吸入空気の流量および遠心式多翼送風機の送風性能は、従来技術における消音部材を有しない遠心式多翼送風機とほぼ同様の高い水準に維持される。   In such a configuration, since the sound deadening member is attached to the outside of the opening end of the air suction port, a part of the noise generated from the centrifugal multiblade fan during air suction is caused by the sound deadening member in the direction toward the inside of the air suction port. However, since the diameter of the opening of the silencer is larger than the diameter of the intake air flow upstream end at the contact portion around the air inlet, the noise reflecting surface of the silencer is tapered. Therefore, the noise is released toward the outside of the air suction port, and the reduction of noise emitted to the outside of the air suction port is efficiently achieved. In addition, since the diameter of the opening of the silencer member is larger than the diameter of the air intake port at the upstream end of the intake air flow, the inner surface of the silencer member is larger than the air intake port over the entire range. The air flow is hardly obstructed by the silencer, and the flow rate of the intake air and the ventilation performance of the centrifugal multiblade fan are maintained at the same high level as the centrifugal multiblade fan without the silencer in the prior art. Is done.

また、とくに限定されないが、上記消音部材の開口部内面には多孔質シート材が貼着されていることが好ましい。このような構成においては、遠心式多翼ファンから発生する騒音の一部が多孔質シート材により吸収されるため、騒音の低減がより効果的に達成される。   Moreover, although it does not specifically limit, it is preferable that the porous sheet material is stuck by the inner surface of the opening part of the said muffling member. In such a configuration, since a part of the noise generated from the centrifugal multiblade fan is absorbed by the porous sheet material, the noise can be reduced more effectively.

本発明に係る消音部材の形状は、空気吸入口を通しての空気吸入流が実質的にほとんど阻害されない形状であればとくに限定されない。例えば、消音部材の開口部は、ベルマウス状に形成されていてもよいし、略円錐台状に形成されていてもよい。   The shape of the sound deadening member according to the present invention is not particularly limited as long as the air suction flow through the air suction port is not substantially hindered. For example, the opening of the muffler member may be formed in a bell mouth shape or may be formed in a substantially truncated cone shape.

本発明に係る遠心式多翼送風機は、とくに限定されないが、例えば、騒音の低減が厳しく要求される、車両空調装置用遠心式多翼送風機として用いられて好適なものである。   The centrifugal multiblade blower according to the present invention is not particularly limited, but is suitable for use as a centrifugal multiblade blower for vehicle air conditioners, for example, in which noise reduction is strictly required.

このように、本発明に係る遠心式多翼送風機によれば、空気吸入口の口径よりも大きい口径を有する消音部材により騒音が装置内部側に向けて反射されるので、騒音の低減が効果的に達成され、しかも、送風性能は従来技術とほぼ同様の高い水準に維持される。   As described above, according to the centrifugal multiblade blower according to the present invention, noise is reflected toward the inside of the apparatus by the silencer member having a diameter larger than the diameter of the air suction port, so that noise reduction is effective. In addition, the air blowing performance is maintained at a high level almost the same as that of the prior art.

以下に、本発明の望ましい実施の形態を、図面を参照して説明する。
図１および図２は、本発明の一実施態様に係る遠心式多翼送風機１を示しており、図１は遠心式多翼送風機１全体の縦断面図を、図２は遠心式多翼送風機１の空気吸入口９近傍における拡大部分断面図を示している。遠心式多翼送風機１は、遠心式多翼ファン２、および遠心式多翼ファン２が収容されるスクロール型のケーシング３からなる。遠心式多翼ファン２は、略円錐形状をなすコーン部４と、コーン部４の外周部に円筒状に多数列設され、一端部分がコーン部４の外周縁部分と連結されたブレード５とを備えている。コーン部４の内側にはモータ６が収納されており、モータ６の回転軸７は、コーン部４の中央部分に穿設されたボス孔８に嵌合されている。モータ６が駆動すると、その回転駆動力は回転軸７を介して遠心式多翼ファン２に伝達され、遠心式多翼ファン２は周方向に回転する。 Hereinafter, preferred embodiments of the present invention will be described with reference to the drawings.
1 and 2 show a centrifugal multiblade fan 1 according to an embodiment of the present invention. FIG. 1 is a longitudinal sectional view of the entire centrifugal multiblade fan 1, and FIG. 2 is a centrifugal multiblade fan. 1 is an enlarged partial cross-sectional view in the vicinity of one air inlet 9. The centrifugal multiblade fan 1 includes a centrifugal multiblade fan 2 and a scroll-type casing 3 in which the centrifugal multiblade fan 2 is accommodated. The centrifugal multiblade fan 2 includes a cone portion 4 having a substantially conical shape, and a blade 5 in which a large number of cylindrical portions are arranged on the outer peripheral portion of the cone portion 4 and one end portion is connected to the outer peripheral edge portion of the cone portion 4. It has. A motor 6 is accommodated inside the cone portion 4, and a rotating shaft 7 of the motor 6 is fitted in a boss hole 8 formed in a central portion of the cone portion 4. When the motor 6 is driven, the rotational driving force is transmitted to the centrifugal multiblade fan 2 via the rotating shaft 7, and the centrifugal multiblade fan 2 rotates in the circumferential direction.

ケーシング３は、上記コーン部４の図１における頂部側と対面する部位に開口された空気吸入口９と、遠心式多翼ファン２の外周部に形成されており、外部の熱交換器ユニット等（図示略）へと連通する空気吐出部１１が設けられたスクロール型の空気通路１０と、を備えている。空気吸入口９を経由して遠心式多翼ファン２の軸方向から吸入された空気は、遠心式多翼ファン２の回転に伴い周方向に複数配列されたブレード５の隙間からファン２の径方向外側へと流出し、遠心式多翼ファン２で得た動圧を空気通路１０内で静圧に変換された後、空気吐出部１１を経由して熱交換器ユニット等へ送出される。   The casing 3 is formed in an air suction port 9 opened at a portion facing the top side of the cone portion 4 in FIG. 1 and an outer peripheral portion of the centrifugal multiblade fan 2, and an external heat exchanger unit or the like. And a scroll type air passage 10 provided with an air discharge portion 11 communicating with (not shown). The air sucked from the axial direction of the centrifugal multiblade fan 2 through the air suction port 9 passes through the gap between the blades 5 arranged in the circumferential direction along with the rotation of the centrifugal multiblade fan 2, and the diameter of the fan 2. After flowing out to the outside in the direction, the dynamic pressure obtained by the centrifugal multiblade fan 2 is converted into a static pressure in the air passage 10 and then sent out to the heat exchanger unit or the like via the air discharge section 11.

空気吸入口９の外側には、吸入空気流上流方向へ開口する開口部１３を有する消音部材１２が付設されている。開口部１３の吸入空気流上流側端部１４における口径（Ｄ２）は空気吸入口９の口径（Ｄ１）よりも大きく形成されており、そのため、消音部材１２は吸入空気流を阻害することはほとんどなく、吸入空気の流量、および多翼送風機１の送風性能は従来技術とほぼ同様の高い水準に維持される。また、開口部１３において、空気吸入口９の周囲に当接する当接部１５の口径（Ｄ３）は、吸入空気流上流側端部１４における口径（Ｄ２）よりも大きく形成されているため、開口部１３の口径は吸入空気流上流側になるほど小さくなり、開口部１３の内面１６は、吸入空気流下流方向、すなわち遠心式多翼ファン２の方向（装置の内部方向）に向けられる。したがって、遠心式多翼ファン２の回転により発生した騒音は、その一部が開口部１３の内面１６により遠心式多翼ファン２方向へ反射されて空気吸入口９外への放出が防止されることとなり、遠心式多翼送風機１の騒音の低減が達成される。   A silencer member 12 having an opening 13 that opens in the upstream direction of the intake air flow is attached to the outside of the air intake port 9. The diameter (D2) at the upstream end 14 of the intake air flow of the opening 13 is formed larger than the diameter (D1) of the air intake 9, so that the silencing member 12 hardly inhibits the intake air flow. In addition, the flow rate of the intake air and the blowing performance of the multiblade blower 1 are maintained at the same high level as in the prior art. Further, in the opening 13, the diameter (D3) of the contact portion 15 that contacts the periphery of the air suction port 9 is formed to be larger than the diameter (D2) in the intake air flow upstream end portion 14. The diameter of the portion 13 decreases as it becomes upstream of the intake air flow, and the inner surface 16 of the opening 13 is directed in the downstream direction of the intake air flow, that is, in the direction of the centrifugal multiblade fan 2 (internal direction of the apparatus). Therefore, a part of the noise generated by the rotation of the centrifugal multiblade fan 2 is reflected toward the centrifugal multiblade fan 2 by the inner surface 16 of the opening 13 and is prevented from being released to the outside of the air inlet 9. As a result, the noise reduction of the centrifugal multiblade fan 1 is achieved.

図１および図２に示されるように、本発明は、実質的に消音部材１２の追加のみで実現可能であるため、既存の遠心式多翼送風機へ容易に適用可能であり、部品コストや組立コストの増加、および遠心式多翼送風機の重量への影響は最小限に抑えられる。   As shown in FIG. 1 and FIG. 2, the present invention can be realized substantially only by adding the silencing member 12, and therefore can be easily applied to an existing centrifugal multiblade fan. The increase in cost and the impact on the weight of the centrifugal multiblade fan is minimized.

また、本実施態様における消音部材１２は、ケーシング３とは異なる部材としてケーシング３の外側に接着されているが、本発明は上記の構成のみに限定されるものではない。例えば、消音部材１２は、締結によりケーシング３に付設されていてもよいし、ケーシング３に一体的に成型された部材として構成されていてもよい。   Moreover, although the sound deadening member 12 in this embodiment is adhere | attached on the outer side of the casing 3 as a member different from the casing 3, this invention is not limited only to said structure. For example, the muffling member 12 may be attached to the casing 3 by fastening, or may be configured as a member formed integrally with the casing 3.

図３は、図１に示した遠心式多翼送風機１の消音部材１２近傍における拡大部分断面図を示しており、図３（Ａ）は消音部材１２がベルマウス状に形成された例を、図３（Ｂ）は消音部材１２が略円錐台状に形成された例を、それぞれ示している。図３において、遠心式多翼ファン２の回転により発生した騒音の音波１７の一部は、開口部１３の内面１６により反射されて反射波１８となる。内面１６へ衝突する際のエネルギー損失により、反射波１８は元の音波１７よりも音のレベルが小さくなる。また、上述の如く、開口部１３の内面１６は遠心式多翼ファン２の方向へ向いているので、反射波１８は遠心式多翼ファン２の方向へ反射され、開口部１３の外部へ漏れることがない。したがって、開口部１３の外部への騒音の拡散が消音部材１２により防止され、騒音の低減が達成される。   FIG. 3 shows an enlarged partial cross-sectional view in the vicinity of the silencing member 12 of the centrifugal multiblade fan 1 shown in FIG. 1, and FIG. 3 (A) shows an example in which the silencing member 12 is formed in a bell mouth shape. FIG. 3B shows an example in which the sound deadening member 12 is formed in a substantially truncated cone shape. In FIG. 3, a part of the noise sound wave 17 generated by the rotation of the centrifugal multiblade fan 2 is reflected by the inner surface 16 of the opening 13 to become a reflected wave 18. Due to energy loss when colliding with the inner surface 16, the reflected wave 18 has a lower sound level than the original sound wave 17. Further, as described above, since the inner surface 16 of the opening 13 faces toward the centrifugal multiblade fan 2, the reflected wave 18 is reflected toward the centrifugal multiblade fan 2 and leaks outside the opening 13. There is nothing. Therefore, noise diffusion to the outside of the opening 13 is prevented by the muffling member 12, and noise reduction is achieved.

図４は、図３（Ｂ）において、開口部１３の内面１６に多孔質シート材１９が貼着された例を示している。図４において、多孔質シート材１９に衝突した音波１７は大部分が吸収されてしまい、多孔質シート材１９により反射される反射波１８は全く存在しないか、存在したとしてもごく僅かとなる。また、内面１６に貼着された多孔質シート材１９の表面は遠心式多翼ファン２の方向へ向いているので、図３の場合と同様、反射波１８は開口部１３の外部へ漏れることがなく、騒音の低減がより効果的に達成される。なお、多孔質シート材１９が貼着される部位は開口部１３の内面１６のみに限定されず、例えば、空気吸入口９の内周面、すなわち、ケーシング３の表面に貼着されていてもよい。   FIG. 4 shows an example in which a porous sheet material 19 is attached to the inner surface 16 of the opening 13 in FIG. In FIG. 4, most of the sound wave 17 that has collided with the porous sheet material 19 is absorbed, and the reflected wave 18 reflected by the porous sheet material 19 does not exist at all or is very small even if it exists. Further, since the surface of the porous sheet material 19 adhered to the inner surface 16 faces the direction of the centrifugal multiblade fan 2, the reflected wave 18 leaks to the outside of the opening 13 as in the case of FIG. And noise reduction is more effectively achieved. In addition, the site | part to which the porous sheet material 19 is affixed is not limited only to the inner surface 16 of the opening part 13, For example, even if it affixes on the inner peripheral surface of the air inlet 9, ie, the surface of the casing 3. Good.

図１に示した実施態様における騒音レベルおよび送風性能の実測値を、従来技術における遠心式多翼送風機と比較した結果を図５に示す。図５の測定においては、まず、従来技術による遠心式多翼送風機の性能が測定された後、同一の遠心式多翼送風機の空気吸入口に消音部材が取り付けられ、本発明に係る遠心式多翼送風機の性能が測定された。測定に用いられた遠心式多翼送風機における空気吸入口の口径（Ｄ１）は９６ｍｍであり、空気吸入口の外側に取り付けられた消音部材としては、開口部の吸入空気流上流側端部における口径（Ｄ２）が１００ｍｍ、開口部における曲率半径が１２．８ｍｍであるベルマウス形状のものが用いられた。図５に示された測定結果においては、本発明の適用により、送風性能を従来技術とほぼ同様の高い水準に維持しつつ（図５（Ｂ））、１．２ｄＢの騒音レベル低減が達成されている（図５（Ａ））。   FIG. 5 shows the result of comparing the measured values of the noise level and the blowing performance in the embodiment shown in FIG. 1 with the centrifugal multiblade fan in the prior art. In the measurement of FIG. 5, first, the performance of a centrifugal multiblade fan according to the prior art is measured, and then a sound deadening member is attached to the air inlet of the same centrifugal multiblade fan. The performance of the wing blower was measured. The diameter (D1) of the air suction port in the centrifugal multiblade fan used for the measurement is 96 mm, and the silencer attached to the outside of the air suction port is the diameter at the upstream end of the suction air flow of the opening. A bell mouth shape with (D2) of 100 mm and a radius of curvature of 12.8 mm at the opening was used. In the measurement results shown in FIG. 5, the application of the present invention achieves a noise level reduction of 1.2 dB while maintaining the air blowing performance at the same high level as that of the conventional technology (FIG. 5B). (FIG. 5A).

本発明は、あらゆる用途における遠心式多翼送風機に適用可能であり、とくに、騒音の低減が厳しく要求される、客室または乗務員室方向へ騒音が波及する車両空調装置用遠心式多翼送風機として好適なものである。   INDUSTRIAL APPLICABILITY The present invention can be applied to a centrifugal multiblade fan for all uses, and is particularly suitable as a centrifugal multiblade fan for a vehicle air conditioner in which noise is severely required and noise is spread toward a passenger cabin or a crew cabin. It is a thing.

本発明の一実施態様に係る遠心式多翼送風機の縦断面図である。It is a longitudinal cross-sectional view of the centrifugal multiblade fan which concerns on one embodiment of this invention. 図１に示した遠心式多翼送風機の空気吸入口近傍における拡大部分断面図である。FIG. 2 is an enlarged partial sectional view in the vicinity of an air inlet of the centrifugal multiblade fan shown in FIG. 1. 図１に示した遠心式多翼送風機の開口部内周面近傍における拡大部分断面図であり、図３（Ａ）は開口部がベルマウス状に形成された例を、図３（Ｂ）は開口部が略円錐台状に形成された例を、それぞれ示している。FIG. 3 is an enlarged partial cross-sectional view in the vicinity of the inner peripheral surface of the opening of the centrifugal multiblade blower shown in FIG. 1, FIG. 3A is an example in which the opening is formed in a bell mouth shape, and FIG. The examples in which the portions are formed in a substantially truncated cone shape are shown. 図３（Ｂ）に示した実施態様において、開口部内周面に多孔質シート材が貼着された場合を例示した部分断面図である。In the embodiment shown in FIG. 3 (B), it is the fragmentary sectional view which illustrated the case where the porous sheet material was stuck by the opening part inner peripheral surface. 従来技術と本発明の性能を比較した特性図であり、図５（Ａ）は騒音レベルの比較、図５（Ｂ）は風量の比較を、それぞれ示している。FIG. 5A is a characteristic diagram comparing the performance of the prior art and the present invention. FIG. 5A shows a comparison of noise levels, and FIG. 5B shows a comparison of air flow.

符号の説明Explanation of symbols

１ 遠心式多翼送風機
２ 遠心式多翼ファン
３ ケーシング
４ コーン部
５ ブレード
６ モータ
７ 回転軸
８ ボス孔
９ 空気吸入口
１０ 空気通路
１１ 空気吐出部
１２ 消音部材
１３ 開口部
１４ 吸入空気流上流側端部
１５ 当接部
１６ 内面
１７ 音波
１８ 反射波
１９ 多孔質シート材 DESCRIPTION OF SYMBOLS 1 Centrifugal multiblade fan 2 Centrifugal multiblade fan 3 Casing 4 Cone part 5 Blade 6 Motor 7 Rotating shaft 8 Boss hole 9 Air inlet 10 Air passage 11 Air discharge part 12 Silencing member 13 Opening part 14 Intake air flow upstream End portion 15 Contact portion 16 Inner surface 17 Sound wave 18 Reflected wave 19 Porous sheet material

Claims (5)

回転軸周りに複数のブレードを有する遠心式多翼ファンと、該遠心式多翼ファンが収納されるスクロールケーシングを有し、該スクロールケーシングに開口された空気吸入口から吸い込まれた空気を前記ブレード間における径方向内側から吸入し径方向外側に吐出する遠心式多翼送風機において、前記スクロールケーシングに開口された空気吸入口の開口端外側に、該空気吸入口の周囲に当接し吸入空気流上流方向へ開口する開口部を有する消音部材が付設されており、該消音部材の開口部においては、吸入空気流上流側端部における口径が前記空気吸入口の口径よりも大きく、前記空気吸入口の周囲への当接部における口径が前記吸入空気流上流側端部における口径よりも大きいことを特徴とする遠心式多翼送風機。   A centrifugal multiblade fan having a plurality of blades around a rotating shaft, and a scroll casing in which the centrifugal multiblade fan is accommodated, and the air sucked from an air suction opening opened in the scroll casing In the centrifugal multiblade fan that sucks in from the radially inner side and discharges in the radially outer direction, the outside of the air suction port that is opened in the scroll casing is in contact with the periphery of the air suction port and the intake air flow upstream A silencing member having an opening that opens in the direction is attached. In the opening of the silencing member, the diameter of the upstream end of the intake air flow is larger than the diameter of the air intake, and the air intake A centrifugal multiblade blower characterized in that a diameter at a contact portion to the periphery is larger than a diameter at an end portion on the upstream side of the intake air flow. 前記消音部材の開口部内面に多孔質シート材が貼着されている、請求項１に記載の遠心式多翼送風機。   The centrifugal multiblade blower according to claim 1, wherein a porous sheet material is adhered to the inner surface of the opening of the silencer member. 前記消音部材の開口部がベルマウス状に形成されている、請求項１または２に記載の遠心式多翼送風機。   The centrifugal multiblade fan according to claim 1 or 2, wherein the opening of the muffler member is formed in a bell mouth shape. 前記消音部材の開口部が略円錐台状に形成されている、請求項１または２に記載の遠心式多翼送風機。   The centrifugal multiblade blower according to claim 1 or 2, wherein the opening of the silencing member is formed in a substantially truncated cone shape. 車両用空調装置内に設けられる、請求項１〜４のいずれかに記載の遠心式多翼送風機。   The centrifugal multiblade fan according to any one of claims 1 to 4, which is provided in a vehicle air conditioner.
JP2008286271A 2008-11-07 2008-11-07 Centrifugal multiblade blower Expired - Fee Related JP5164801B2 (en)

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Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012112299A (en) * 2010-11-24 2012-06-14 Mitsubishi Electric Corp Multiblade centrifugal fan and multiblade centrifugal blower
JP2016035261A (en) * 2014-07-31 2016-03-17 ジェンサーム インコーポレイテッドＧｅｎｔｈｅｒｍ Ｉｎｃｏｒｐｏｒａｔｅｄ Suction port boundary surface of air mover, and cover

Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05106893A (en) * 1991-10-18 1993-04-27 Matsushita Seiko Co Ltd Ventilating fan
JP2006077723A (en) * 2004-09-13 2006-03-23 Matsushita Electric Ind Co Ltd Multi-blade fan

Patent Citations (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPH05106893A (en) * 1991-10-18 1993-04-27 Matsushita Seiko Co Ltd Ventilating fan
JP2006077723A (en) * 2004-09-13 2006-03-23 Matsushita Electric Ind Co Ltd Multi-blade fan

Cited By (2)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JP2012112299A (en) * 2010-11-24 2012-06-14 Mitsubishi Electric Corp Multiblade centrifugal fan and multiblade centrifugal blower
JP2016035261A (en) * 2014-07-31 2016-03-17 ジェンサーム インコーポレイテッドＧｅｎｔｈｅｒｍ Ｉｎｃｏｒｐｏｒａｔｅｄ Suction port boundary surface of air mover, and cover

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