JP2007255865A - Air conditioner - Google Patents

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JP2007255865A
JP2007255865A JP2006084559A JP2006084559A JP2007255865A JP 2007255865 A JP2007255865 A JP 2007255865A JP 2006084559 A JP2006084559 A JP 2006084559A JP 2006084559 A JP2006084559 A JP 2006084559A JP 2007255865 A JP2007255865 A JP 2007255865A
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resonance
air
blower
silencer
air conditioner
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JP4925698B2 (en
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Yoshinori Nakagawa
祥道 中川
Masahiko Nakagawa
昌彦 中川
Hajime Fujimoto
肇 藤本
Hiroshi Nakada
浩 中田
Keisuke Sotozono
圭介 外囿
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Mitsubishi Electric Corp
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Mitsubishi Electric Corp
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Abstract

<P>PROBLEM TO BE SOLVED: To reduce low frequency air distribution noise caused by rotation of an air blower in an air conditioner. <P>SOLUTION: In this air conditioner where a heat exchanger 5 and the air blower 1 are received in a housing 9, and the air exchanging heat in the heat exchanger 5 is supplied from the housing 9 by the air blower 1, at least one resonance type silencer 2 arousing resonance to specific frequency of noise caused by rotation of rotary blades 4 constituting the air blower 1, is disposed at a suction-side, a supply-side or both of the suction side and supply side of the air blower 1. <P>COPYRIGHT: (C)2008,JPO&INPIT

Description

この発明は、空気調和装置に係り、特にその送風音の低減に関するものである。   The present invention relates to an air conditioner, and more particularly to reduction of the blowing sound.

従来の空気調和装置において、その送風音（又は送風騒音）に対しては、グラスウール等の吸音材を、騒音伝播部分である風路に配置して対処している（例えば、特許文献１参照）。
特開平11−248183号公報（第６頁、第６図など） In the conventional air conditioner, the blowing sound (or blowing noise) is dealt with by arranging a sound absorbing material such as glass wool in the air passage that is a noise propagation portion (for example, see Patent Document 1). .
Japanese Patent Laid-Open No. 11-248183 (page 6, FIG. 6 etc.)

しかしながら、従来の場合、送風機の回転数に依存する低周波送風音に対しては、吸音材の特性上、吸音性能が低く、十分な消音効果が得られない場合が多い。
また、空気調和装置内部に十分な大きさの吸音材を配置することが困難な場合についても同様に消音効果が得られない。
また、小型の空気調和装置の風路内部に吸音材を配置すると、それが風路抵抗となり風量低下を招いたり、局所風速の増加により吸音材が飛散することがあり、飛散を防止する対策が必要になる等の問題があった。
さらに、屋外に設置する機器においては、風路内に風雨、太陽光等が進入し、吸音材を劣化させるという問題点があった。 However, in the conventional case, with respect to the low-frequency blowing sound depending on the rotation speed of the blower, the sound absorbing performance is low due to the characteristics of the sound absorbing material, and a sufficient silencing effect is often not obtained.
In addition, the silencing effect cannot be obtained in the same manner even when it is difficult to arrange a sufficiently large sound absorbing material inside the air conditioner.
In addition, if a sound absorbing material is placed inside the air path of a small air conditioner, it may become a wind path resistance, leading to a reduction in the air volume, or the sound absorbing material may be scattered due to an increase in local wind speed. There were problems such as being necessary.
Furthermore, in the equipment installed outdoors, there is a problem that wind and rain, sunlight, etc. enter the air passage and deteriorate the sound absorbing material.

この発明は、上記のような課題を解決するためになされたもので、低周波数の特定送風音を効果的に低減することができる空気調和装置を得ることを第１の目的とする。
また、グラスウール等の吸音材を使用せずに、低周波数の特定送風音の低減を図ることを第２の目的とする。 This invention was made in order to solve the above subjects, and makes it the 1st objective to obtain the air conditioning apparatus which can reduce the specific blowing sound of a low frequency effectively.
A second object is to reduce low-frequency specific blowing sound without using a sound absorbing material such as glass wool.

この発明に係る空気調和装置は、熱交換器と送風機が筐体内に収納され、前記送風機により前記熱交換器で熱交換された空気が前記筐体から吹き出される空気調和装置において、前記送風機の吸込み側、吹出し側、又は吸込み側と吹出し側の両方の送風音伝播路に、前記送風機を構成する回転翼の回転に起因する送風音の特定周波数に対して共鳴を生ずる少なくとも１つの共鳴型消音器を配置したものである。   An air conditioner according to the present invention is an air conditioner in which a heat exchanger and a blower are housed in a housing, and air heat-exchanged by the heat exchanger by the blower is blown out of the housing. At least one resonance-type silencer that causes resonance with respect to a specific frequency of the blowing sound caused by the rotation of the rotor blades constituting the blower in the suction side, the blowing side, or the blowing sound propagation path on both the suction side and the blowing side A container is placed.

この発明の空気調和装置は、共鳴型消音装置を送風機の吸込み側、吹出し側、又は吸込み側と吹出し側の両方の送風音伝播路に配置したので、グラスウール等の吸音材なしで、特定周波数の送風音が共鳴によって大幅に低下するという効果を奏する。   In the air conditioner of the present invention, the resonance type silencer is disposed on the suction side of the blower, the blowout side, or the blowing sound propagation path on both the suction side and the blowout side. There is an effect that the blowing sound is greatly reduced by resonance.

実施の形態１．
図１はこの発明の実施の形態１における空気調和装置の構成を示す平面図（ａ）、正面図（ｂ）、側面図（ｃ）である。また、図２はこの発明の実施の形態１で使用する共鳴型消音器の正面図（ａ）、側面図（ｂ）である。
図１における空気調和装置１０、熱交換器５と送風機１が筐体９内に収納されており、熱交換器５には熱交換器５へ冷媒を供給する冷媒配管６が接続されている。そして、筐体９の外部から内部に導入した空気を、熱交換器５で熱交換し、送風機１を利用して筐体９の外へ吹き出す構成としている。送風機１は複数枚（その枚数をZとする）の回転翼４を備え、筐体１０内の風路３に配置されて、空気調和装置内における空気の流れを作り出している。 Embodiment 1 FIG.
1 is a plan view (a), a front view (b), and a side view (c) showing the configuration of an air-conditioning apparatus according to Embodiment 1 of the present invention. FIG. 2 is a front view (a) and a side view (b) of the resonance silencer used in the first embodiment of the present invention.
The air conditioner 10, the heat exchanger 5, and the blower 1 in FIG. 1 are housed in a housing 9, and a refrigerant pipe 6 that supplies a refrigerant to the heat exchanger 5 is connected to the heat exchanger 5. The air introduced from the outside of the housing 9 is heat-exchanged by the heat exchanger 5 and blown out of the housing 9 using the blower 1. The blower 1 includes a plurality of rotor blades 4 (the number of which is Z) and is arranged in the air passage 3 in the housing 10 to create an air flow in the air conditioner.

ここでは、送風機１の空気吸込み側と空気吹出し側の両方の風路３に共鳴型消音器２を複数配置している。ただし、送風音の状況や程度に応じて、空気吸込み側または空気吹出し側だけに、共鳴型消音器２を１以上配置する態様としてもよい。
空気調和装置１０内に配置された共鳴型消音器２は、装置１０内で風路３を構成しており、その風路３は送風音伝播路となっている。
共鳴型消音器２は、例えば図２に示すような筒体構造をしており、開口端部を開口部２１、中空の内部を空洞部２２、空洞部２２を形成する外郭を外郭部２３と称するものとする。この共鳴型消音器２は、その開口端を送風機１から送られる空気の流路（又は回転翼４が配置された風路）の縁部に位置させて配置するのが好ましい。 Here, a plurality of resonant silencers 2 are arranged in the air passage 3 on both the air suction side and the air blowing side of the blower 1. However, it is good also as an aspect which arrange | positions one or more resonance type silencers 2 only to the air suction side or the air blowing side according to the condition and grade of blowing sound.
The resonance-type silencer 2 arranged in the air conditioner 10 constitutes an air path 3 in the apparatus 10, and the air path 3 is a blowing sound propagation path.
The resonance silencer 2 has a cylindrical structure as shown in FIG. 2, for example. The opening end is an opening 21, the hollow interior is a cavity 22, and the outer wall forming the cavity 22 is an outer wall 23. Shall be called. The resonance silencer 2 is preferably arranged with its open end positioned at the edge of the flow path of the air sent from the blower 1 (or the air path in which the rotor blades 4 are arranged).

次に、図１に示した空気調和装置１０の動作について説明する。空気調和装置１０が運転を開始すると、送風機１の回転翼４が回転する。これにより、図１中の矢印方向に空気の流れが生じる。すなわち、筐体９の外部から内部に導入された空気は、熱交換器５、風路３、送風機１を経て、筐体９の外部に放出される。このとき熱交換器５では、冷媒配管６より供給される冷媒と矢印のように流れる空気との間で熱交換が行われる。   Next, the operation of the air conditioner 10 shown in FIG. 1 will be described. When the air conditioner 10 starts operation, the rotary blade 4 of the blower 1 rotates. Thereby, an air flow is generated in the direction of the arrow in FIG. That is, the air introduced into the inside from the outside of the housing 9 is discharged to the outside of the housing 9 through the heat exchanger 5, the air path 3, and the blower 1. At this time, in the heat exchanger 5, heat exchange is performed between the refrigerant supplied from the refrigerant pipe 6 and the air flowing as shown by the arrows.

このとき、送風機１では、回転翼４の回転数をNとすると、N×Zを基本周波数ｆ1とし、その高調波成分ｆ2、ｆ3‥を含む回転音（送風音）が発生する。回転音は、一般的に周囲の騒音成分より大きなパルス波形を示す。この回転音は、空気調和装置１０の風路３を介して、風路３における空気の流れの上流方向及び下流方向へそれぞれ伝播する。その際、共鳴型消音器２の空洞部８内で、特定周波数の送風音に対して共鳴が起こり、それにより特定周波数の送風音は熱となって消散する。   At this time, in the blower 1, assuming that the rotational speed of the rotary blade 4 is N, N × Z is set as a fundamental frequency f1, and a rotating sound (blowing sound) including the harmonic components f2, f3. The rotating sound generally shows a pulse waveform larger than the surrounding noise component. The rotating sound propagates through the air passage 3 of the air conditioner 10 in the upstream direction and the downstream direction of the air flow in the air passage 3. At that time, resonance occurs in the hollow portion 8 of the resonance silencer 2 with respect to the blowing sound of the specific frequency, and thereby the blowing sound of the specific frequency is dissipated as heat.

周波数ｆの回転音が低減できる騒音レベルLは、共鳴型消音器２の空洞部長さh、空洞部断面積p、送風機１から共鳴型消音器２までの距離d、風路３の断面積qを用いて、以下の式で決定できる。
L=10・log((SIN(k・d)+p/q・COS(k・d)・TAN(k・h))2+(COS(k・d))2)
ただし、ｋ＝２πｆ/ｃ ｃ：音速 （ｃ＝331.5・√（1+ｔ/273）） ｔ：温度（℃） The noise level L at which the rotational sound of the frequency f can be reduced includes the cavity length h of the resonance silencer 2, the cavity cross sectional area p, the distance d from the blower 1 to the resonance silencer 2, and the cross sectional area q of the air passage 3. Can be determined by the following equation.
L = 10 ・ log ((SIN (k ・ d) + p / q ・ COS (k ・ d) ・ TAN (k ・ h)) 2 + (COS (k ・ d)) 2 )
Where k = 2πf / c c: speed of sound (c = 331.5 · √ (1 + t / 273)) t: temperature (° C.)

従って、低減したい回転音の周波数で共鳴を生ずるように、騒音レベルLの式中に示した距離d、長さh及び断面積p,qを調整した共鳴型消音器２を、回転音の伝播経路中に配置することで、目的の送風音を低減することができる。実施の形態１は、この原理を利用して、送風機１の回転に起因する特定周波数の送風音を低減したものである。実施の形態１の空気調和装置による送風音は、図４に示す波形となった。図４からは、Ａ点（７５０Ｈｚ）付近での回転音が大きく減少していることが分かる。   Therefore, the resonance muffler 2 in which the distance d, the length h and the cross-sectional areas p and q shown in the formula of the noise level L are adjusted so that resonance is generated at the frequency of the rotation sound to be reduced is transmitted to the rotation sound. By arranging in the route, the target blowing sound can be reduced. Embodiment 1 uses this principle to reduce the blowing sound of a specific frequency resulting from the rotation of the blower 1. The blowing sound by the air conditioner of Embodiment 1 has the waveform shown in FIG. From FIG. 4, it can be seen that the rotational sound near point A (750 Hz) is greatly reduced.

実施の形態２．
実施の形態１では、送風機１の回転音の伝播経路中に、回転音の特定周波数成分で共鳴を生ずる共鳴型消音器２を配置した。しかし、騒音レベルLの式より明らかなように、低減できる周波数は、共鳴型消音器２の周囲温度により異なる。従って、ある温度ｔにおいて目的とする送風音の周波数成分を低減するように調整した共鳴型消音器の場合、空気調和装置内のように周囲温度が大きく変化する環境においては、共鳴周波数と低減したい送風音の周波数が一致しなくなり、十分な減音が得られない場合がある。実施の形態２では、この影響まで考慮した空気調和装置を提案する。 Embodiment 2. FIG.
In the first embodiment, the resonance type silencer 2 that resonates at a specific frequency component of the rotating sound is disposed in the propagation path of the rotating sound of the blower 1. However, as is clear from the expression of the noise level L, the frequency that can be reduced varies depending on the ambient temperature of the resonance silencer 2. Therefore, in the case of a resonance silencer adjusted so as to reduce the frequency component of the target blowing sound at a certain temperature t, it is desired to reduce the resonance frequency in an environment where the ambient temperature changes greatly as in an air conditioner. In some cases, the frequency of the blowing sound does not match, and sufficient sound reduction cannot be obtained. The second embodiment proposes an air conditioner that takes this effect into consideration.

図５はある共鳴型消音器２の減音量（騒音の低減量）の周波数特性と空気調和装置で使用される空気温度（空調温度）との関係を示すグラフである。ここでは、空気温度として、15℃、20℃、25℃及び30℃が選ばれている。このグラフから、空気温度が高いほど減音量が最大となる周波数は、高周波数側にずれることがわかる。しかし、上記の各温度に応じて、共鳴型消音器２の空洞部２２の長さｈを30〜120mm、空洞部２１の断面積ｐを15〜2800mm2の範囲で変更してその仕様を変えることで、図６に示すように、温度が異なった場合においても、減音量が最大となる周波数を同一となるように調整することができる。 FIG. 5 is a graph showing the relationship between the frequency characteristic of the volume reduction (noise reduction amount) of a certain resonance silencer 2 and the air temperature (air conditioning temperature) used in the air conditioner. Here, 15 ° C., 20 ° C., 25 ° C. and 30 ° C. are selected as the air temperature. From this graph, it can be seen that the higher the air temperature, the higher the frequency at which the volume reduction is maximized. However, according to each temperature, the length h of the cavity 22 of the resonance silencer 2 is changed within the range of 30 to 120 mm, and the cross-sectional area p of the cavity 21 is changed within the range of 15 to 2800 mm 2 to change the specifications. Thus, as shown in FIG. 6, even when the temperatures are different, the frequency at which the volume reduction is maximum can be adjusted to be the same.

図７はこの発明の実施の形態２に係る空気調和装置の構成図であり、図６のような減音特性が得られるように、送風機１の周囲に、異なる仕様の複数の共鳴型消音器を配置した例を示している。図７中、共鳴型消音器２a、２b、２c、２ｄは、図６におけるA仕様、B仕様、C仕様、D仕様の減音特性を持つ消音器であり、送風機１の周囲に配置されて風路３を構成している。
この空気調和装置において、熱交換器５を通過した空気は、例えば温度15℃〜30℃の範囲で変動して送風機１を通過する。この場合、送風機１で発生した回転音の減音度と温度の関係は、図８の破線で表すように、空調温度範囲の全域で高い減音度を維持できる。図８には各共鳴型消音器２a、２b、２c、２ｄの減音度と温度との関係が示されており、各共鳴型消音器２a、２b、２c、２ｄを組み合わせた場合の減音度と温度との関係は、破線で表された状態となる。なお、図８中、共鳴型消音器２aだけ使用した場合の減音度と温度の関係は白三角（△印）付き太線で表わされ、共鳴型消音器２ｂ、２ｃ、２ｄだけを使用した場合は、それぞれ、白丸（○）付き実線、白四角（□）付き実線、米印（＊）付き実線で表わされる。 FIG. 7 is a block diagram of an air conditioner according to Embodiment 2 of the present invention, and a plurality of resonance silencers of different specifications are provided around the blower 1 so as to obtain a sound reduction characteristic as shown in FIG. The example which has arranged is shown. In FIG. 7, resonance silencers 2 a, 2 b, 2 c, and 2 d are silencers having sound reduction characteristics of A specification, B specification, C specification, and D specification in FIG. 6, and are arranged around the blower 1. An air passage 3 is formed.
In this air conditioner, the air that has passed through the heat exchanger 5 fluctuates, for example, in a temperature range of 15 ° C. to 30 ° C. and passes through the blower 1. In this case, the relationship between the temperature reduction degree of the rotating sound generated by the blower 1 and the temperature can maintain a high sound reduction degree throughout the air-conditioning temperature range, as represented by the broken line in FIG. FIG. 8 shows the relationship between the sound reduction degree of each resonance-type silencer 2a, 2b, 2c, and 2d and the temperature, and the sound reduction when each resonance-type silencer 2a, 2b, 2c, and 2d is combined. The relationship between degree and temperature is represented by a broken line. In FIG. 8, the relationship between the sound reduction and the temperature when only the resonance silencer 2a is used is represented by a thick line with white triangles (Δ mark), and only the resonance silencers 2b, 2c, and 2d are used. Each case is represented by a solid line with a white circle (◯), a solid line with a white square (□), and a solid line with an asterisk (*).

以上のように、実施の形態２の空気調和装置によれば、使用温度範囲内の所定の温度毎に同じ低周波数に対して減音量が最大となるように調整した、仕様の異なる複数の共鳴型消音器を風路３へ配置しているので、空気調和装置の空調温度範囲の全域で高い減音度を維持し、回転音を低減することができる。   As described above, according to the air-conditioning apparatus of the second embodiment, a plurality of resonances having different specifications that are adjusted so that the volume reduction is maximized with respect to the same low frequency for each predetermined temperature within the operating temperature range. Since the type silencer is arranged in the air passage 3, a high sound reduction degree can be maintained in the entire air conditioning temperature range of the air conditioner, and the rotational noise can be reduced.

実施の形態３．
ここでは、共鳴型消音器２の配置位置に関する効果的な態様を提案する。図９はこの発明の実施の形態３に係る空気調和装置における共鳴型消音器２の配置位置の関係を示す模式図である。ここでは、共鳴型消音器２は送風機１から送られる空気の流路より僅かに外側にずれた位置に配置している。この「ずれ量」をLdで表すこととし、ずれ量Ldを、0mm、10mm、30mm、50mmにした場合の送風音の周波数特性を示すグラフを、それぞれ図４、図１０、図１１、図１２に示した。また、ここでの共鳴型消音器２は、回転音の１次成分を低減するように調整されたものを使用している。 Embodiment 3 FIG.
Here, the effective aspect regarding the arrangement position of the resonance type silencer 2 is proposed. FIG. 9 is a schematic diagram showing the relationship of the arrangement position of the resonance silencer 2 in the air-conditioning apparatus according to Embodiment 3 of the present invention. Here, the resonance silencer 2 is disposed at a position slightly shifted outward from the flow path of the air sent from the blower 1. This “deviation amount” is represented by Ld, and graphs showing the frequency characteristics of the blowing sound when the deviation amount Ld is 0 mm, 10 mm, 30 mm, and 50 mm are shown in FIGS. 4, 10, 11, and 12, respectively. It was shown to. The resonance silencer 2 used here is adjusted so as to reduce the primary component of the rotating sound.

図４、図１０、図１１、図１２を、共鳴型消音器を備えていない従来の空気調和装置の場合の図３と比較してみると、共鳴型消音器２を配置することにより、Ａ点（周波数７５０Ｈｚ付近）のピーク値が低下していることがわかる。ただし、Ld=0（図４）やLd=10（図１０）の場合、Ｂ領域（４００−６００Ｈｚ付近）での低周波側の騒音は図３に比較して目立って増加している。これは、送風機１からの吹き出し空気が、共鳴型消音器２へ衝突することにより空気流れに乱れを生じ、その乱れによる圧力変動により生じたものである。これを防止するためには、共鳴型消音器２の位置を送風機１から送られる空気の流路より外側にずらして配置し、共鳴型消音器２へ衝突する空気の量を減らすのが有効である。例えば、Ld＝30mm（図１１）やLd＝50mm（図１２）の場合には、Ａ点のピーク値が図３の場合より低下しており、かつLd=0の場合よりＢ領域の騒音もかなり低下している。従って、実施の形態３では、送風機１から送られる空気の流路から外側にずれた位置に共鳴型消音器２を配置した空気調和装置を提案する。この場合の共鳴型消音器２の「ずれ量」は、好ましくはLd＝30mm以上、特に好ましくはLd＝50mm以上とし、かつ共鳴型消音器２の共鳴消音効果が得られる範囲内とする。   4, 10, 11, and 12 are compared with FIG. 3 in the case of a conventional air conditioner that does not include a resonance silencer, by arranging the resonance silencer 2, A It can be seen that the peak value at the point (frequency around 750 Hz) is lowered. However, when Ld = 0 (FIG. 4) or Ld = 10 (FIG. 10), the noise on the low frequency side in the B region (around 400-600 Hz) is remarkably increased as compared with FIG. This is because the air blown from the blower 1 collides with the resonance silencer 2 to cause disturbance in the air flow, and is caused by pressure fluctuation due to the disturbance. In order to prevent this, it is effective to shift the position of the resonance silencer 2 to the outside of the air flow path sent from the blower 1 to reduce the amount of air colliding with the resonance silencer 2. is there. For example, when Ld = 30 mm (FIG. 11) or Ld = 50 mm (FIG. 12), the peak value at point A is lower than in FIG. 3, and the noise in the B region is also lower than when Ld = 0. It has dropped considerably. Therefore, Embodiment 3 proposes an air conditioner in which the resonance silencer 2 is disposed at a position shifted outward from the flow path of the air sent from the blower 1. In this case, the “deviation amount” of the resonance silencer 2 is preferably Ld = 30 mm or more, particularly preferably Ld = 50 mm or more, and within a range in which the resonance silencer 2 can obtain the resonance silencer effect.

以上のように、実施の形態３の空気調和装置は、送風機１から送られる空気の流路から僅かに外側にずれた位置に共鳴型消音器２を配置するようにしているので、送風機１の回転音を低減できると共に、共鳴型消音器２の影響で増加する空気流の乱れに起因する騒音も抑制することができる。   As described above, the air conditioner of the third embodiment is arranged such that the resonance silencer 2 is disposed at a position slightly shifted outward from the flow path of the air sent from the blower 1. Rotational noise can be reduced, and noise caused by turbulence in the air flow that increases due to the influence of the resonance silencer 2 can be suppressed.

実施の形態４．
実施の形態４では、共鳴型消音器自体の形状の各種態様を提案する。代表的な共鳴型消音器２は、実施の形態１で示したような円筒形をなし、その一端面を閉塞したものである。そのような形状であれば、図１３に示すように、一般的な配管部材である円管（外郭部２３を構成）とキャップ２４にて構成でき、安価に騒音低減を図ることができる。なお、共鳴型消音器２の空洞部２３に、多孔質材料２５を挿入することにより減音効果を高めることも可能である。さらに、図１４に示すように、共鳴型消音器２の端面を非平行面として、複数の共鳴周波数を得るように構成することも可能である。この他、共鳴型消音器２として、図１５に示すような形状のへルムホルツ型消音器を使用しても実施の形態１〜３と同様な効果を得ることができる。 Embodiment 4 FIG.
In the fourth embodiment, various aspects of the shape of the resonant silencer itself are proposed. A typical resonance silencer 2 has a cylindrical shape as shown in the first embodiment and has one end face closed. If it is such a shape, as shown in FIG. 13, it can be comprised with the circular pipe (outer part 23 is comprised) and the cap 24 which are general piping members, and can aim at noise reduction at low cost. Note that the sound reduction effect can be enhanced by inserting the porous material 25 into the cavity 23 of the resonance silencer 2. Furthermore, as shown in FIG. 14, it is also possible to obtain a plurality of resonance frequencies by using the end face of the resonance silencer 2 as a non-parallel surface. In addition, even if a Helmholtz type silencer having a shape as shown in FIG. 15 is used as the resonance type silencer 2, the same effects as those of the first to third embodiments can be obtained.

この発明の実施の形態１に係る空気調和装置の主な構成を示す平面図（ａ）、正面図（ｂ）、側面図（ｃ）。The top view (a) which shows the main structures of the air conditioning apparatus which concerns on Embodiment 1 of this invention, a front view (b), and a side view (c). 実施の形態１で使用する共鳴型消音器の構造を示す正面図（ａ）、側面図（ｂ）。The front view (a) which shows the structure of the resonance-type silencer used in Embodiment 1, and a side view (b). 従来の空気調和装置における送風音の周波数特性を示すグラフ。The graph which shows the frequency characteristic of the ventilation sound in the conventional air conditioning apparatus. 実施の形態１による送風音の周波数特性を示すグラフ（Ld=0mmの場合）。The graph which shows the frequency characteristic of the ventilation sound by Embodiment 1 (when Ld = 0mm). 同一仕様の共鳴型消音器の温度に依存する減音特性を示すグラフ。The graph which shows the sound reduction characteristic depending on the temperature of the resonance type silencer of the same specification. 同一周波数に対して最大の減音特性が得られるよう温度毎に調整した共鳴型消音器の減音特性を示すグラフ。The graph which shows the noise reduction characteristic of the resonance type silencer adjusted for every temperature so that the maximum noise reduction characteristic with respect to the same frequency is obtained. 実施の形態２に係る空気調和装置の主な構成を示す平面図（ａ）、側面図（ｂ）。The top view (a) which shows the main structures of the air conditioning apparatus which concerns on Embodiment 2, and a side view (b). この発明の実施の形態２に係る空気調和装置の減音特性を示すグラフ。The graph which shows the sound reduction characteristic of the air conditioning apparatus which concerns on Embodiment 2 of this invention. この発明の実施の形態３に係る空気調和装置内における共鳴型消音器の配置例示図。The example of arrangement | positioning of the resonance type silencer in the air conditioning apparatus which concerns on Embodiment 3 of this invention. 流路からのずれ量Ld=10mm時の騒音の周波数特性を示すグラフ。The graph which shows the frequency characteristic of the noise when deviation | shift amount Ld = 10mm from a flow path. 流路からのずれ量Ld=30mm時の騒音の周波数特性を示すグラフ。The graph which shows the frequency characteristic of the noise when deviation | shift amount Ld = 30mm from a flow path. 流路からのずれ量Ld=50mm時の騒音の周波数特性を示すグラフ。The graph which shows the frequency characteristic of the noise when deviation | shift amount Ld = 50mm from a flow path. 共鳴型消音器の構造例１を示す正面図（ａ）と側面図（ｂ）。The front view (a) and side view (b) which show structural example 1 of a resonance type silencer. 共鳴型消音器の構造例２のその１を示す側面図（ａ）とその２を示す側面図（ｂ）。The side view (a) which shows the 1 of the structural example 2 of a resonance type silencer, and the side view (b) which shows the 2 共鳴型消音器の構造例３を示す正面図（ａ）と側面図（ｂ）。The front view (a) and side view (b) which show structural example 3 of a resonance type silencer.

符号の説明Explanation of symbols

１ 送風機、２ 共鳴型消音器、３ 風路、４ 送風機の回転翼、５ 熱交換器、６ 冷媒配管、９ 筐体、１０ 空気調和装置、２１ 共鳴型消音器の開口部、２２ 共鳴型消音器の空洞部、２３ 共鳴型消音器の外郭部、２４ キャップ、２５ 多孔質材料。
DESCRIPTION OF SYMBOLS 1 Blower, 2 Resonance type silencer, 3 Air path, 4 Rotor blade, 5 Heat exchanger, 6 Refrigerant piping, 9 Case, 10 Air conditioner, 21 Resonance type silencer opening, 22 Resonance type silencer Cavity of the vessel, 23 Outer part of the resonance type silencer, 24 Cap, 25 Porous material.

Claims (5)

熱交換器と送風機が筐体内に収納され、前記送風機により前記熱交換器で熱交換された空気が前記筐体から吹き出される空気調和装置において、
前記送風機の吸込み側、吹出し側、又は吸込み側と吹出し側の両方の送風音伝播路に、前記送風機を構成する回転翼の回転に起因する送風音の特定周波数に対して共鳴を生ずる少なくとも１つの共鳴型消音器を配置したことを特徴とする空気調和装置。 In the air conditioner in which the heat exchanger and the blower are housed in a housing, and the air heat-exchanged by the heat exchanger by the blower is blown out of the housing.
At least one that causes resonance with respect to a specific frequency of the blowing sound caused by the rotation of the rotor blades constituting the blower in the blowing sound propagation path on the suction side, the blowing side, or both the suction side and the blowing side of the blower An air conditioner comprising a resonance silencer. 空調温度範囲内の異なる複数の温度毎に共鳴特性の異なる複数の共鳴型消音器を配置し、各共鳴型消音器が同じ特定周波数に対して共鳴を生ずるようにしたことを特徴とする請求項１記載の空気調和装置。   A plurality of resonance silencers having different resonance characteristics are arranged for each of a plurality of different temperatures within an air conditioning temperature range, and each resonance silencer generates resonance at the same specific frequency. The air conditioning apparatus according to 1. 前記送風機から送られる空気の流路から外側にずれた位置に、前記共鳴型消音器を配置したことを特徴とする請求項１又は２記載の空気調和装置。   The air conditioner according to claim 1 or 2, wherein the resonance silencer is arranged at a position shifted outward from a flow path of air sent from the blower. 前記共鳴型消音器を円筒形として、その一端面を閉塞した構造としたことを特徴とする請求項１〜３のいずれかに記載の空気調和装置。   The air-conditioning apparatus according to any one of claims 1 to 3, wherein the resonance silencer has a cylindrical shape and has one end face closed. 前記共鳴型消音器の内部に多孔質材料を挿入した構造としたことを特徴とする請求項１〜４のいずれかに記載の空気調和装置。
The air conditioner according to any one of claims 1 to 4, wherein a porous material is inserted into the resonance silencer.
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CN114811888A (en) * 2021-01-21 2022-07-29 中国船舶重工集团公司第七一一研究所 Noise control method for self-cooling type air blower room

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JPH0450498A (en) * 1990-06-20 1992-02-19 Matsushita Electric Ind Co Ltd Noise eliminator for cross-flow blower
JPH0635478A (en) * 1992-06-26 1994-02-10 Tokyo Electric Co Ltd Vacuum cleaner
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Publication number Priority date Publication date Assignee Title
CN114811888A (en) * 2021-01-21 2022-07-29 中国船舶重工集团公司第七一一研究所 Noise control method for self-cooling type air blower room
CN114811888B (en) * 2021-01-21 2024-03-22 中国船舶集团有限公司第七一一研究所 Self-cooling type blower room noise control method

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