JPS5841415B2 - tunnel tunnel - Google Patents
tunnel tunnelInfo
- Publication number
- JPS5841415B2 JPS5841415B2 JP49147472A JP14747274A JPS5841415B2 JP S5841415 B2 JPS5841415 B2 JP S5841415B2 JP 49147472 A JP49147472 A JP 49147472A JP 14747274 A JP14747274 A JP 14747274A JP S5841415 B2 JPS5841415 B2 JP S5841415B2
- Authority
- JP
- Japan
- Prior art keywords
- blades
- noise
- sound
- tunnel
- distance
- Prior art date
- Legal status (The legal status 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 status listed.)
- Expired
Links
Landscapes
- Structures Of Non-Positive Displacement Pumps (AREA)
- Ventilation (AREA)
Description
【発明の詳細な説明】
本発明は同一の軸流ファンを使用した排気装置に関する
もので、モータの両側の羽根からの騒音を羽根相互の音
の干渉によって減少させることを目的とする。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to an exhaust system using the same axial fan, and its purpose is to reduce noise from blades on both sides of a motor through sound interference between the blades.
従来トンネル用等の排気装置は騒音を減少させるため吸
込側あるいは吐出側にグラスウールなどの吸音材を内貼
した消音筒が使用されているが吸音材の特質上１０００
Ｈｚ前後の騒音はある程度減少するが１００〜３００Ｈ
ｚ前後の騒音は減少しない欠点を有していた。Conventionally, in order to reduce noise, exhaust systems for tunnels, etc., use a sound-absorbing tube lined with sound-absorbing material such as glass wool on the suction or discharge side, but due to the characteristics of the sound-absorbing material,
Noise around Hz is reduced to some extent, but at 100-300H
The problem was that the noise around z was not reduced.
これは回転数×羽根枚数Ｘ１／６０＝羽根騒音ｆＨｚの
ためであり、１００〜３００ Ｈｚ前後の騒音が高いも
のであった。This is because the number of rotations x the number of blades x 1/60 = blade noise fHz, and the noise was high around 100 to 300 Hz.
又、騒音の低減を図る方法として、回転軸に複数段の翼
車な設け、各翼車には枚数がそれぞれ異なるように動翼
を設けてファンの静圧を高め、騒音を低減せしめるもの
もあるが、数種類の翼車を必要とするためコスト高にな
ると共に翼車のアンバランスによる振動が増加したり、
調整に手間がかかる欠点があった。Another method of reducing noise is to install multiple stages of impellers on the rotating shaft, and each impeller has a different number of moving blades to increase the static pressure of the fan and reduce noise. However, it requires several types of impellers, which increases costs and increases vibration due to unbalanced impellers.
The drawback was that it took a lot of time to adjust.
本発明は前記従来の欠点を除去するものであり以下本発
明の一実施例につき添付図面に沿って詳細に説明する。The present invention eliminates the above-mentioned drawbacks of the conventional art, and one embodiment of the present invention will be described in detail below with reference to the accompanying drawings.
１はトンネル内に設けられる消音筒ケース、２は前記消
音筒ケース１内に内貼される吸音材、３は前記吸音材２
の内径側に装着されるパンチングメタル、４，５はモー
タ６の両側に取り付けた軸流ファンの羽根、なお軸流フ
ァンの羽根４，５は同一である。Reference numeral 1 denotes a sound-absorbing tube case provided in the tunnel, 2 a sound-absorbing material attached inside the noise-reducing tube case 1, and 3 a sound-absorbing material 2.
The punching metals 4 and 5 attached to the inner diameter side of the motor 6 are the blades of an axial fan attached to both sides of the motor 6, and the blades 4 and 5 of the axial fan are the same.
ｌは前記羽根４，５間の距離である。そして羽根４，５
間の距離ｌは羽根騒音ｆ（羽根の回転数×羽根枚数／６
０）の波長（音速／ｆ）の１／２に設定すれば、羽根相
互間の干渉により騒音を減少させることができるもので
ある。l is the distance between the blades 4 and 5. and feathers 4,5
The distance l between them is the blade noise f (rotational speed of the blade x number of blades/6
If the wavelength is set to 1/2 of the wavelength (sound velocity/f) of 0), noise can be reduced due to interference between the blades.
いま例えば羽根枚数を６枚とし、回転数を１７００ ｒ
ｐｍとすれば、羽根騒音ｆＨｚは６×１７０ ｏ、’
６０＝１７０Ｈｚとなり、その波長は音速Ｃを３４０ｍ
／ｓとすればＣ／ｆ＝３４０／１７０−＝２ｍとなる。For example, let's say the number of blades is 6 and the rotation speed is 1700 r.
pm, the blade noise fHz is 6×170 o,'
60=170Hz, and its wavelength is the speed of sound C at 340m.
/s, C/f=340/170-=2m.
この波長の１／２は１ｍとなるので羽根４，５０間の距
離ｌは！！ ＝ １ ｍとなるものである。Since 1/2 of this wavelength is 1 m, the distance l between the blades 4 and 50 is! ! = 1 m.
このように羽根４，５間の距１［を１ｍに設定すれば第
２図のように羽根相互間の騒音の干渉によって騒音が除
去されるものである。In this way, if the distance 1 between the blades 4 and 5 is set to 1 m, noise will be removed by interference between the blades as shown in FIG.
第２図は横軸に時間ｔをとり縦軸に騒音のエネルギーＥ
をとったものであり、実線は羽根４かもの騒音を示し、
点線は羽根５かもの騒音を示している。In Figure 2, the horizontal axis represents time t, and the vertical axis represents noise energy E.
The solid line indicates the noise of four blades,
The dotted line shows the noise of the five blades.
そして第２図によればどの点をとってみても羽根４と羽
根５の干渉により騒音が打消されており騒音が除去され
ることが明白である。According to FIG. 2, it is clear that the noise is canceled out by the interference between the blades 4 and 5 no matter which point is taken.
第３図に羽板間隔を波長の１／２とした時の回転音減少
のデータを示す。Figure 3 shows data on reduction in rotational noise when the blade spacing is set to 1/2 of the wavelength.
この場合、回転数Ｎ＝１７００（ｒｐｍ ）、羽根枚数
Ｚ＝６に回転音周波数ｆ−Ｎ −ｚ ／ ６０ ＝ １
７０ （Ｈｚ ）、波長λ＝Ｃ７ｆ票２ｍとする。In this case, the rotational speed N = 1700 (rpm), the number of blades Z = 6, and the rotational sound frequency f - N -z / 60 = 1
70 (Hz), wavelength λ=C7f 2m.
第３図において、実線は従来例でｌ中０．７ｍ、破線は
本発明で羽根間距離ｌ＝λ／２（中１ ｍ ）とした例
であり、回転音（１次、２次）が４〜８ｄＢ減少する。In Fig. 3, the solid line is the conventional example with a distance of 0.7 m in l, and the broken line is the example of the present invention where the distance between the blades is l = λ/2 (1 m in the middle), and rotational noise (primary and secondary) is It decreases by 4-8dB.
このように本発明は同一の軸流ファンなモータの両側に
取付け、２個の軸流ファンの羽根の距離を羽根騒音ｆＨ
ｚ（羽根の回転数×羽根枚数／６０）の波長（音速／７
）の１／２に設定したもので、羽根相互間の干渉によっ
て騒音を除去することができ静かな運転を行なうことが
できると共に同一の軸流ファンを使用することが出来る
ので、枚数がそれぞれ異なる動翼を設けたファンを使用
して騒音の低減を図るものに比較して、コストも安く、
ファンのアンバランスによる振動も無く、ファンの調整
に手間がかかることも無い等の優れた効果が発揮される
ものである。In this way, the present invention installs the same axial fan on both sides of the motor, and adjusts the distance between the blades of the two axial fans to determine the blade noise fH.
Wavelength of z (speed of rotation x number of blades/60) (velocity of sound/7
) is set to 1/2 of Compared to a fan with rotor blades that reduces noise, it is cheaper and
Excellent effects such as no vibration due to unbalanced fan and no time-consuming adjustment of the fan are exhibited.
第１図は本発明の一実施例であるトンネル用排気装置の
側断面図、第２図は同装置の羽根の騒音特性図、第３図
は従来例と本発明との比較による音圧レベル対、周波数
の特性図である。
１・・・・・・消音筒ケース、４，５・・・・・・軸流
ファンの羽根、６・・・・・・モータ、ｌ・・・・・・
羽根間の距離。Fig. 1 is a side sectional view of a tunnel exhaust system which is an embodiment of the present invention, Fig. 2 is a noise characteristic diagram of the blades of the same device, and Fig. 3 is a comparison of sound pressure levels between a conventional example and the present invention. FIG. 2 is a characteristic diagram of frequency. 1... Silence cylinder case, 4, 5... Axial flow fan blade, 6... Motor, l...
distance between blades.
Claims (1)
に取り付け、２個の軸流ファンの羽根間の距離を羽根騒
音ｆＨ２（羽根の回転数×羽根枚数／６０）の波長（音
速／ｆ）の１／２に設定した排気装置。1 Install the same axial fans on both sides of the motor in the noise-reducing cylinder case, and calculate the distance between the blades of the two axial fans as the wavelength (sound velocity/f) of the blade noise fH2 (rotational speed of blades x number of blades/60). ) Exhaust system set to 1/2.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP49147472A JPS5841415B2 (en) | 1974-12-20 | 1974-12-20 | tunnel tunnel |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP49147472A JPS5841415B2 (en) | 1974-12-20 | 1974-12-20 | tunnel tunnel |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5173746A JPS5173746A (en) | 1976-06-25 |
| JPS5841415B2 true JPS5841415B2 (en) | 1983-09-12 |
Family
ID=15431148
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP49147472A Expired JPS5841415B2 (en) | 1974-12-20 | 1974-12-20 | tunnel tunnel |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5841415B2 (en) |
Families Citing this family (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5462509A (en) * | 1977-10-27 | 1979-05-19 | Agency Of Ind Science & Technol | Blower-noise reducing method by phase control |
| JPH0732636Y2 (en) * | 1989-12-29 | 1995-07-26 | 株式会社荏原製作所 | Silencer |
Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4898411A (en) * | 1972-03-27 | 1973-12-14 |
-
1974
- 1974-12-20 JP JP49147472A patent/JPS5841415B2/en not_active Expired
Patent Citations (1)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS4898411A (en) * | 1972-03-27 | 1973-12-14 |
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5173746A (en) | 1976-06-25 |
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