1227763 ⑴ 玖、發明說明 【發明所屬之技術領域】 本發明是關於在空調機的室內單元所具備的橫流風扇 【先前技術】 近年來，空調機是被要求省電化與靜音化，作爲其中 一個卽省電力的方法’增大將與流動於熱交換器內的冷媒 進行熱交換的室內空氣吹出室內單元外的吹出風扇的風量 的方法。作爲室內單元的風扇的壁掛式空調機，其主流方 式是使用橫流風扇（c r 0 S S f 1 0 w f a η )。如習知的，如果增 加該室內單元的風扇的風量的話，會讓室內熱交換器的熱 交換性能提昇。如果能不增大風扇轉數而增大風扇的風量 的話，結果能提昇空調機全體的性能而產生與省電（不改 變消耗電力）相同的空調效果。 作爲增大該室內單元的吹風機的風量的方法，則考慮 有如上述的提昇室內單元的送風機也就是橫流風扇的轉數 、以及增大風扇的外徑的方法。 由於室內單元作動時的亂流聲音（分布於高頻的頻寬 區域的聲音），是與橫流風扇的轉數的7〜8次方成比例 ，在前者的方法中使風量產生3 0 %的情況，會增加9 d Β。 另一方面，由於亂流聲音是與橫流風扇的外徑的4〜5次 方成比例，在後者的方法中使風量產生3 0 °/°的情況’會增 加 5dB。 (2) 1227763 結果，要使風量增大而盡可能的不使噪音（亂流聲音 )增加是後者的方法較妥當。可是，室內單元的尺寸是有 限制的，因此具備於室內單元的內側的橫流風扇的大小也 有限制，是加大外徑並不容易。如果將橫流風扇的外徑加 大到極限的話，會由於橫流風扇與筒口之間的間隙變小而 產生顯著的雜音（葉片片數Z與旋轉數N ( /sec )的乘積 所產生的頻率Z . N ( Hz )，或是其高次的頻率）、以及 由於室內熱交換器與橫流風扇的距離太近讓橫流風扇的葉 片接近，讓橫流風扇的葉片接近尾流區域（通過熱交換器 的氣流的速度分布在管部下流較緩慢，其位置是速度分布 很大變化的區域），由於葉片通過該區域而會產生聲音， 會有這樣的問題。 因此，作爲用來抑制以上的橫流風扇的干擾所造成的 葉片聲音來減低噪音的習知技術，如習知的專利文獻1、 2。這兩個文獻，雖然效果不相同而其原理是相同的，即 使爲了增加風量而增大橫流風扇讓筒口間隙變小，也有抑 制噪音（葉片聲音）的效果。 也就是說，其原理，是藉由相對於旋轉軸方向來使橫 流風扇的葉片外徑變化，使橫流風扇的葉片外周前端構造 傾斜於筒口，藉由該傾斜，讓葉片外周前端通過筒口（或 尾流區域）時，會產生時間差（相位差）。 藉由將從葉片外周前端與筒口的位置關係所產生的週 期性的聲音時間性地分散，則可以抑制葉片聲音，則可減 小筒口間隙而達到高風量化。 (3) 1227763 作爲其他習知技術，像習知的專利文獻3、4。來說 明這些公報所記載的內容。爲了防止橫流風扇的葉片聲音 ，將葉片的圓周方向安裝間距作成不等間隔，藉由使各葉 片的圓周方向的相位相異，則可抑制峰値聲音可減低全體 的噪音。 記載於這些專利文獻1、專利文獻2、專利文獻3、 及專利文獻4的低噪音、高風量化的技術其方式雖然不相 同’而要使葉片聲音週期性地分散這方面卻是共通的，減 低噪音（葉片聲音）的部分會使風量增加，可以提昇空調 機的的性能。 【專利文獻1】 曰本特開平9一 1 00795號公報 【專利文獻2】 曰本特開2 00 1 —5 0 1 8 9號公報 【專利文獻3】 曰本特開平6— 1 293 8 7號公報 【專利文獻4】 曰本特開平6— 1 7 3 8 8 6號公報 【發明內容】 【發明欲解決的課題】 可是近年來，空調機是被要求要更加省電化、靜音化 (低噪音、高風量化），因此需要更高效率、低噪音的橫 流風扇。而橫流風扇的聲音會有流體所產生的寬頻區域的 -9- (4) 1227763 亂流聲音，即使可以像上述習知技術抑制週期性的葉片聲 音，也不能減低該亂流聲音。因此僅以習知技術中的方法 ，是很難實現降低噪音、且節省電力的目的。 本發明的目的，是要提供一種室內空調，要減低流體 造成的亂流聲音讓噪音降低，藉由高風量化來節省電力。 【用以解決課題的手段】 針對在室內單元內具備有橫流風扇的空調機，表示上 述橫流風扇的葉片剖面的厚度中心的彎曲線包括兩個圓弧 ，是藉由使各個圓弧的彎曲方向互相反轉來達成上述目的 〇 針對在室內單元內具備有橫流風扇的空調機，是使構 成上述橫流風扇的葉片的壓力面相對於旋轉軸方向是一致 的，來達成上述目的。 針對在室內單元內具備有橫流風扇的空調機，是將葉 片的厚度設定成’讓上述橫流風扇的葉片間流路寬度其外 徑側相對於內徑側是6 0〜8 0 %的範圍。 第二手段’針對具備有作爲室內單元的吹風機的橫流 風扇的空調機，是使構成風扇的葉片的壓力面相對於旋轉 軸方向是一致的構造。藉由使壓力面一致，則旋轉軸方向 的速度分布不會很混亂而能調整其平衡性，有助於提昇橫 流風扇的性能。 第三手段’針對具備有作爲室內單元的吹風機的橫流 風扇的空調機，風扇的葉片間流路寬度其外徑側相對於內 -10- (5) 1227763 徑側是作成在60〜80%變化的構造。橫流風扇基本上是朝 向吹出側流體的速度會越來越增加的增速翼列，藉由其葉 片間流路寬度來決定流體速度增加的程度，會對橫流風扇 的性能造成很大的影響。 第四手段’爲了提高降低噪音的效果，除了上述三個 手段的其中之一之外’是作成相對於旋轉軸方向來使風扇 的葉片外徑變化的構造。藉由使葉片外徑變化，藉由對葉 片的干涉施加時間差（相位差），則可以抑制葉片聲音且 讓噪音降低。 【實施方式】 以下根據第1圖〜第8圖來說明本發明的一實施例。 第1圖是顯示室內空調室內單元全體，（a)是從正 面來看的全體圖’ （b)是顯示從室內單元來看的剖面。 單元全體是被裝飾框2覆蓋，是作成以過濾器5、熱交換 器6、橫流風扇1的順序，包覆在內的構造，在橫流風扇 1的下方設置有殻體7。 橫流風扇1的大槪外觀是顯示於第2圖，（c )是顯 示全體的形狀’ （d )是顯示從旋轉軸方向來看的剖面。 是將在圓周方向配置葉片1 2的圓板1 3當作一個風扇區塊 ’藉由在旋轉軸方向組合數個風扇區塊來構成一個橫流風 扇1。在風扇的兩端安裝具備有端面圓板1 4與轂部1 6的 轂部端面圓板1 5 ’將端面圓板1 4作爲軸承側旋轉，將轂 部v而面0板1 5作爲馬達軸側旋轉。 -11 - (6) l227763 在單元的實際運轉狀態，在第1圖（b )上，橫流風 扇1是藉由馬達1 0而向順時鐘方向旋轉，從設置於裝飾 框2的前面格栅3與上面格柵4吸入空氣，從單元下部的 吹出口送風。在單元內部的氣流，會經由過濾器5到達熱 交換器6，在通過熱交換器6的過程中會被冷卻、或被加 熱。經過熱交換的氣流穿過橫流風扇1會流向殼體7側， 在吹出口附近會藉由縱風向板8與橫風向板9控制其風向 讓其吹出。 第3圖、第4圖、第5圖是顯示本發明的橫流風扇的 特徵，是從旋轉軸方向來看橫流風扇1的剖面的放大圖。 以下記載其內容。 在第3圖，表示葉片12的厚度中心的彎曲線1 7，是 由曲率半徑爲ρ 1與P 2的兩個圓弧所構成’是分別使圓弧 的相反方向反轉。而達成某片12的厚度的分布’從翼長 的中腹部朝向葉片外周前端、葉片內周前端依序變薄而形 成葉片形狀。 著眼於流體的性質，一般來說，流速越快則亂流聲音 越大，則需要的輸入也會增加。關於亂流聲音會顯示在以 下的數學式子（1 ) ’是根據通過ί頁流風扇的某片則彡而的 流速（代表速度）v ( m/s) ° SPioclogb.K)…（數學式 1) α是：,變換係數，也就是會由於流體機械的種類、狀態1227763 玖 发明 Description of the invention [Technical field to which the invention belongs] The present invention relates to a cross-flow fan provided in an indoor unit of an air conditioner [prior art] In recent years, air conditioners have been required to save power and mute, as one of them 卽Power-saving method 'A method of increasing the air volume of a blow-out fan that blows indoor air that is in heat exchange with the refrigerant flowing in the heat exchanger out of the indoor unit. As a wall-mounted air conditioner for a fan of an indoor unit, a mainstream method is to use a cross flow fan (c r 0 S S f 1 0 w f a η). As is known, if the air volume of the fan of the indoor unit is increased, the heat exchange performance of the indoor heat exchanger will be improved. If the air volume of the fan can be increased without increasing the number of fan revolutions, the overall performance of the air conditioner can be improved, and the same air-conditioning effect as power saving (without changing power consumption) can be produced. As a method of increasing the air volume of the hair dryer of the indoor unit, the above-mentioned methods of increasing the number of revolutions of the blower, that is, the cross-flow fan of the indoor unit, and increasing the outer diameter of the fan are considered. The turbulent sound (sound distributed in the high-frequency bandwidth area) when the indoor unit is operating is proportional to the 7-8 power of the cross-flow fan's revolution. In the former method, the air volume is 30%. In this case, it will increase by 9 d Β. On the other hand, since the turbulent sound is proportional to the 4-5th power of the outer diameter of the cross-flow fan, the case where the air volume is generated by 30 ° / ° in the latter method 'will increase by 5dB. (2) 1227763 As a result, it is more appropriate to increase the air volume without increasing the noise (turbulent sound) as much as possible. However, since the size of the indoor unit is limited, the size of the cross-flow fan provided inside the indoor unit is also limited, and it is not easy to increase the outer diameter. If the outer diameter of the cross-flow fan is increased to the limit, a significant noise will be generated because the gap between the cross-flow fan and the nozzle becomes smaller (the frequency Z generated by the product of the number of blades Z and the number of rotations N (/ sec)). N (Hz), or its higher frequency), and because the distance between the indoor heat exchanger and the cross flow fan is too close, the blades of the cross flow fan are close, and the blades of the cross flow fan are close to the wake area (through the heat exchanger). The velocity distribution of the airflow is relatively slow downstream in the tube section, and its position is an area where the velocity distribution is greatly changed. Because the blade passes through this area, sound will be generated, and there will be such a problem. Therefore, as a conventional technique for suppressing the noise of the blades caused by the interference of the above-mentioned cross-flow fan to reduce the noise, the conventional patent documents 1 and 2 are known. Although the effects of these two documents are different, the principles are the same. Even if the cross-flow fan is increased to increase the air volume to reduce the gap between the nozzles, it also has the effect of suppressing noise (blade sound). In other words, the principle is to change the outer diameter of the blade of the cross-flow fan with respect to the direction of the rotation axis, so that the tip structure of the outer periphery of the blade of the cross-flow fan is inclined to the nozzle. In the wake region), a time difference (phase difference) occurs. By periodically dispersing the periodic sound generated from the positional relationship between the tip of the outer periphery of the blade and the mouthpiece, the blade sound can be suppressed, and the mouthpiece gap can be reduced to achieve high wind quantization. (3) 1227763 As another conventional technique, it is like the conventional patent documents 3 and 4. The contents described in these bulletins will be explained. In order to prevent the blade sound of the cross-flow fan, the installation pitch in the circumferential direction of the blade is made at unequal intervals. By making the phases in the circumferential direction of each blade different, the peak noise can be suppressed and the overall noise can be reduced. Although the low-noise and high-wind quantization technologies described in Patent Literature 1, Patent Literature 2, Patent Literature 3, and Patent Literature 4 have different methods, it is common for the blade sound to be dispersed periodically. Reducing the noise (blade sound) will increase the air volume and improve the performance of the air conditioner. [Patent Document 1] Japanese Patent Publication No. 9-1 00795 [Patent Literature 2] Japanese Patent Publication No. 2 00 1 -5 0 1 8 9 [Patent Literature 3] Japanese Patent Publication No. 6-1 293 8 7 [Patent Document 4] Japanese Unexamined Patent Publication No. 6-1 7 3 8 8 6 [Summary of the Invention] [Problems to be Solved by the Invention] However, in recent years, air conditioners have been required to be more power-saving and quieter (lower Noise, high wind quantification), so more efficient, low noise cross flow fans are needed. The cross-flow fan's sound will have a -9- (4) 1227763 turbulence in a wide frequency range generated by the fluid. Even if the periodic blade sound can be suppressed as in the conventional technique described above, the turbulence cannot be reduced. Therefore, it is difficult to achieve the purpose of reducing noise and saving power only by the methods in the conventional technology. An object of the present invention is to provide an indoor air conditioner, which reduces noise caused by turbulent flow caused by fluids, reduces noise, and saves power by high wind quantization. [Means to Solve the Problem] For an air conditioner having a cross flow fan in an indoor unit, the bending line indicating the thickness center of the cross section of the blade of the cross flow fan includes two arcs, and the bending direction of each arc is set by Reciprocating each other to achieve the above-mentioned object. For an air conditioner including a cross-flow fan in an indoor unit, the pressure surfaces of the blades constituting the cross-flow fan are made uniform with respect to the direction of the rotation axis to achieve the above object. For an air conditioner having a cross-flow fan in an indoor unit, the thickness of the blade is set to ‘the width of the flow path between the blades of the cross-flow fan is such that the outer diameter side is within a range of 60 to 80% with respect to the inner diameter side. The second means' is an air conditioner including a cross flow fan having a hair dryer as an indoor unit, and has a structure in which a pressure surface of a blade constituting the fan is uniform with respect to a direction of a rotation axis. By making the pressure surfaces uniform, the speed distribution in the direction of the rotation axis will not be confused and its balance can be adjusted, which helps to improve the performance of the cross-flow fan. The third method is for an air conditioner including a cross-flow fan with a hair dryer as an indoor unit. The width of the fan-to-blade flow path has an outer diameter side relative to the inner -10- (5) 1227763. The diameter side is changed by 60 to 80%. The construction. A cross-flow fan is basically a speed-increasing wing that increases the speed of the fluid toward the blow-out side. The width of the flow path between the blades determines the degree of increase in fluid speed, which will greatly affect the performance of the cross-flow fan. The fourth means "in order to improve the noise reduction effect, in addition to one of the above three means" has a structure in which the outer diameter of the fan blade is changed with respect to the direction of the rotation axis. By changing the outer diameter of the blade and applying a time difference (phase difference) to the interference of the blade, the blade sound can be suppressed and the noise can be reduced. [Embodiment] An embodiment of the present invention will be described below with reference to Figs. 1 to 8. Fig. 1 is a diagram showing the entire indoor air-conditioning indoor unit, and (a) is an entire diagram viewed from the front side; (b) is a cross-sectional diagram viewed from the indoor unit. The entire unit is covered with a decorative frame 2 and has a structure including a filter 5, a heat exchanger 6, and a cross flow fan 1. The housing 7 is provided below the cross flow fan 1. The external appearance of the cross-section fan 1 is shown in Fig. 2 and (c) shows the overall shape '(d) shows a cross section viewed from the direction of the rotation axis. The circular plate 1 3 in which the blades 12 are arranged in the circumferential direction is regarded as one fan block ′, and a plurality of fan blocks are combined in the direction of the rotation axis to form a cross-flow fan 1. At both ends of the fan, a hub portion end plate 1 5 with end plates 16 and a hub portion 16 is mounted. The end surface plate 14 is rotated as a bearing side, and the hub portion v and the surface plate 15 are used as motors. Shaft side rotation. -11-(6) l227763 In the actual operating state of the unit, in Figure 1 (b), the cross-flow fan 1 is rotated in the clockwise direction by the motor 10, from the front grille 3 provided on the decorative frame 2. The air is sucked into the upper grille 4 and blown through the air outlet from the lower part of the unit. The air flow inside the unit passes through the filter 5 to the heat exchanger 6, and is cooled or heated while passing through the heat exchanger 6. The heat-exchanged air flows through the cross-flow fan 1 to the casing 7 side, and the wind direction is controlled by the wind direction plate 8 and the cross-direction plate 9 near the air outlet to let it blow out. Figs. 3, 4 and 5 show the features of the cross flow fan according to the present invention, and are enlarged views of the cross section of the cross flow fan 1 when viewed from the direction of the rotation axis. The contents are described below. In Fig. 3, a bending line 17 showing the thickness center of the blade 12 is composed of two arcs having curvature radii ρ 1 and P 2 ', and the directions of the arcs are reversed, respectively. The thickness distribution of a certain sheet 12 is reached from the mid-abdomen of the wing length toward the front end of the outer periphery of the blade, and the front end of the inner periphery of the blade is sequentially thinned to form the shape of the blade. Focusing on the nature of the fluid, generally speaking, the faster the flow velocity, the louder the turbulent sound, and the more input required. The turbulent sound will be shown in the following mathematical formula (1) 'It is based on the flow velocity (representing speed) of a piece passing through a page flow fan (representing speed) v (m / s) ° SPioclogb.K) ... 1) α is :, the conversion coefficient, which is due to the type and state of fluid machinery
而採取不同的定値。因此’噪音値SPL會由於代表速度V -12- (7) 1227763 Π嚷數値有很大的變化。在室內空調所使用的橫流風扇如果 將其代表速度V減少；! 0%的話，則能使噪音値減少3dB。 關於輸入會顯示在以下的數學式子（2 )，是根據通過橫 流風扇的葉片所吹出的流速（代表速度）V。 p，V2 W = P + ^^-…（數學式2)And take a different fix. Therefore, the 'noise' SPL varies greatly due to the representative speed V -12- (7) 1227763 Π 嚷 number. If the cross-flow fan used in the indoor air conditioner reduces its representative speed V;! 0%, it can reduce the noise 値 by 3dB. The input is shown in the following formula (2), which is based on the flow velocity (representing speed) V blown out by the blades of the cross flow fan. p, V2 W = P + ^^ -... (Equation 2)
w是每單位體積給予到流體的輸入（w/m3 ) ，p、P 是代表流體區域的壓力（Pa )與密度（kg/m3 )。在大氣 中運轉室內空調的狀態，壓力p在上流側、下流側是近似 於大氣壓力可以考慮幾乎沒有影響。而在室內空調的橫流 風扇的送風性能，流體可以看成非壓縮所以密度p是一定 的，對輸入W有很大影響的因素，是從橫流風扇吹出的 代表速度V。因此，當流量一定時，使用在寬廣區域將流 體送出而讓流速V降低的話，可以減低輸入w。當輸入w 一定時，在寬廣的區域送出流體可以流出更多的流量。 由上述可得知’如果將橫流風扇1的葉片剖面形狀的 中心線1 7作成以兩個圓弧反轉的構造的話，最大流速區 域的殼體7側的葉片外周附近的流出區域會被擴大’可以 將流體廣泛且緩慢地送出。在此說明僅以一個圓弧所形成 的葉片（例如’在第3圖僅以P2形成）的相異之處。來 對使用以一個圓弧所形成的葉片的橫流風扇的流動進行分 析，求出最外周的葉片間（從鄰接的旋轉方向的前方的葉 片的前端到運算對象葉片的前端）的流速分布。其流速分 $ #不zp均，可得知運算對象的葉片前端附近的流速較快 -13- (8) 1227763 。如前述，流速會直接影響到噪音，由於僅有一部分是高 速流並不會有助於全體風量。因此，在本實施例中’藉由 使葉片的外周側前端彎曲向半旋轉方向則可抑制之前突出 的高速流動。 結果，會成爲低噪音化、高效率，藉由節省電力、增 加風量而可提升空調機的性能。針對其送風性能的效果如 以下所示。第6圖是顯示，在第2圖（d)中橫流風扇1 朝順時鐘方向轉動的情況，曲率半徑p 1與效率η的關係 ，橫軸是採取當將曲率半徑Ρ2的彎曲方向當作正値時的 曲率半徑ρ 1的倒數，縱軸是採取效率比η/η 〇。（ η 0是表 示以往橫流風扇的效率，針對以往的風扇是在第8圖加以 說明。）作爲性能評價的指標的效率η是表示爲橫流風扇 的風扇效率的數學式子（3 )。w is the input (w / m3) given to the fluid per unit volume, and p, P are the pressure (Pa) and density (kg / m3) representing the fluid area. In a state where the indoor air conditioner is operated in the atmosphere, the pressure p is close to the atmospheric pressure on the upstream side and the downstream side, and it is considered that there is almost no influence. In the cross-flow fan of indoor air conditioners, the fluid can be regarded as non-compressed, so the density p is constant, and the factor that greatly affects the input W is the representative speed V blown out by the cross-flow fan. Therefore, when the flow rate is constant, if the flow rate V is reduced by sending the fluid out over a wide area, the input w can be reduced. When the input w is constant, sending out fluid in a wide area can flow out more flow. From the above, it can be understood that if the center line 17 of the cross-sectional shape of the blade of the cross-flow fan 1 is configured with two arcs reversed, the outflow area near the outer periphery of the blade on the casing 7 side of the maximum flow rate area will be enlarged 'The fluid can be delivered widely and slowly. Here, the differences between the blades formed with only one arc (for example, 'formed only with P2 in Fig. 3) will be described. The flow of a cross-flow fan using blades formed by one arc is analyzed, and the flow velocity distribution between the outermost blades (from the tip of the blade in front of the adjacent rotation direction to the tip of the calculation target blade) is obtained. The flow velocity is divided into $ # and zp, and it can be known that the flow velocity near the tip of the blade of the operation object is faster -13- (8) 1227763. As mentioned above, the flow velocity directly affects the noise, because only a part of it is high-speed flow and does not contribute to the overall air volume. Therefore, in this embodiment, 'the high-speed flow protruding before can be suppressed by bending the outer peripheral side tip of the blade in a half rotation direction. As a result, noise reduction and high efficiency can be achieved, and the performance of the air conditioner can be improved by saving power and increasing the amount of air. The effect on the air supply performance is shown below. Fig. 6 shows the relationship between the radius of curvature p 1 and the efficiency η when the cross-flow fan 1 rotates clockwise in Fig. 2 (d). The horizontal axis is taken as the positive direction of the curvature of the radius of curvature P2. The reciprocal of the radius of curvature ρ 1 at ， takes the efficiency ratio η / η 〇 on the vertical axis. (Η 0 is the efficiency of the conventional cross-flow fan, and the conventional fan is described in Figure 8.) The efficiency η, which is an index for performance evaluation, is a mathematical expression (3) expressed as the efficiency of the fan of the cross-flow fan.
AP-Q …（數學式3) Γ ·ω 式中的Pt爲全壓（Pa ) ，Q爲流量（m3/s ) ，τ爲橫 流風扇的扭力（N · m ) ，ω是表示橫流風扇的角速度（ rad/s )，針對全壓pt再展開爲數學式（4 )。AP-Q… (mathematical formula 3) Γ · ω where Pt is total pressure (Pa), Q is the flow rate (m3 / s), τ is the torque of the cross-flow fan (N · m), and ω is the cross-flow fan. The angular velocity (rad / s) is re-expanded into the mathematical formula (4) for the total pressure pt.
Px^Ps+Pd - Pd = —…（數學式4) 全壓P t是表示爲靜壓p s與動壓P d的和，動壓p d則 是藉由密度P與代表速度V所決定的。如上述可以把效 率η整理爲數學式（5 )的形式。 -14- (9) 1227763 η^{ΑΡ^^~-)^ΐ(Τ^ω)-(數學式5) 當給予了流量Q —定，旋轉數一定（角速度ω —定 )的條件時，藉由：從上流側到下流側的靜壓變化ΔΡδ、 代表速度變化AV2、橫流風扇的扭力Τ則決定了效率η。 在第6<圖的性能評價中，流量、旋轉數是一定的，不管是 任何情況的葉片形狀其壓力面爲一致，最大厚度値是固定 的，葉片外徑、最小內徑則是固定的，是給予了內外徑比 爲一定的條件。旋轉軸方向的葉片外周的變化狀態是採取 直線地變化的第4圖（f)所示的型態，是給予了 D! <D2 的條件，在全部的條件中，從D !到D 2的變化率是相等的 。因此可由第6圖，將曲率半徑作爲參數來評價送風性能 ，判斷在形成有葉片剖面形狀的中心線1 7的兩圓弧的曲 率半徑互相反轉的負的區域爲最大效率點。也就是說，葉 片1 2的外周前端爲彎曲反轉的形狀則會有提昇橫流風扇 1的性能的效果，會有助於空調機的性能提昇。 在第4圖（e )中，兩個描繪的葉片1 2的剖面，是分 別對於旋轉軸方向在任意位置的剖面，該位置顯示在從半 控方向來看一個區塊的剖面圖（f )。較厚較大的剖面 A 是表示一個風扇區塊的圓板 3側，較薄較小的剖面 A，是 表示其相反側。藉由其剖面圖，可以看出壓力面1 8相對 於旋轉軸方向是大致一致的。而在（f )中广相對於旋轉 軸方向的外徑變化從直徑D !到直徑D 2是直線性地變化， 其關係之所以爲D ! #D2是要用來加上先前技術所示使葉片 (10) 1227763 聲音降低的效果。一般來說，在送風機的葉片的壓力面的 部分’是流體直接施加動力的區域，會對送風性能有很大 的影響。該壓力面爲歪斜狀態的話，流體平衡性會很差而 不均勻的流動會很強，結果會產生性能降低、噪音增大這 樣的問題。這種問題，是由於上述的流體性質所引起的， 根本上可以藉由相同的原理來解決。針對其內容以下加以 說明。由之前所敘述的數學式子（1 ) 、（ 2 )來判斷，噪 音値、輸入會受到代表速度V的很大影響。因此，流速V 越大則噪音會增大，輸入也會增加。這裡是著重於流出於 葉片間的流體的旋轉軸方向的速度分布。當對於旋轉軸方 向其壓力面歪斜的狀態時，其形狀爲主要原因，，速度分布 會對於旋轉軸方向有很大的變化。相反地，當對於旋轉軸 方向其壓力面一致時，速度分布會大致均勻，流體會以一 樣的流速流出。此時將流量當作一定，來比較雙方的速度 分布，針對對性能造成的影響在下面加以說明。壓力面歪 斜的葉片，相對於從流量計算出來的平、均流速 Vave存在 有局部流速 V快速的區域與緩慢的區域，該速度分布的 各微小區域的輸入，在速度快速的區域會很大，在速度小 的區域會很小。如數學式子（2 )所示，輸入是以流速的 二次方增加，其速度分布，在高速區域的$俞入增加部·分是 比低速區域的輸入減低部分更多，結果，總輸入是比全體 均勻的速度分布的輸入更大。也就是說，壓力面一致的葉 片，相對於從流量所計算的平均流速vave全體會成爲大 致相同的流速（vave)，關於速度分布也可說是輸入最少 -16- (11) 1227763 的狀態。即使從噪音方面來考慮，如數學式（1 )所示， 壓力面歪斜的葉片，由於存在有流速 v較快的區域，會 讓噪音增加，而壓力面一致的葉片會成爲噪音値最低的速 度分布。從速度分布的觀點來看的話，壓力面在旋轉軸方 向一致的某片其速度分布會是一樣的，輸入、噪苜都會是 在最好的狀態。於是，如上述藉由讓壓力面1 8朝向旋轉 軸方向，則能改善流體的平衡性，能提昇送風性能，實現 靜音性。 藉由限定葉片的流路寬度則能使性能提昇，在第5圖 說明其內容。在（g )所示的葉片間流路寬度B，在葉片 內徑側爲最大寬度Bmax，在葉片外徑側爲最小寬度BmiN 。最大寬度B m a X ’是藉由將（h )所示的葉片內徑r i N與 葉片內徑前端、旋轉軸作爲基點所決定的'葉片間隔θ而表 示爲Bmax = r*iNsiN0，最小寬度BmiN則定義爲葉片外徑側的 最小寬度。在該狀態，在第7圖顯示僅將流路寬度1變化比 率BmiN/Bmax作爲參數來評價風扇性能的效果。葉片最大 厚度是固定的，葉片內徑、外徑也是固定的，來給予了內 外徑比爲一定的條件，葉片內徑、外徑的兩端也作成任何 條件都相等的形狀（同樣是R )來加以比較。效率η是與 上述針對送風性能所不的橫流風扇的風扇效率η的家義相 同，從橫流風扇的上流側到下流側的壓力變化與流·量，是 錯由風扇所給予的扭力與旋轉數所決定的。這裡針對效率 η與流路覓度變化比半BmiN/Bmax的關係來加以說明。在 橫流風扇的吹出口附近，由於流量Q是一定的，所以 -17- (12) 1227763Px ^ Ps + Pd-Pd = —... (Equation 4) The total pressure P t is expressed as the sum of the static pressure p s and the dynamic pressure P d, and the dynamic pressure p d is determined by the density P and the representative speed V. As described above, the efficiency η can be arranged into the form of mathematical formula (5). -14- (9) 1227763 η ^ {ΑΡ ^^ ~-) ^ ΐ (Τ ^ ω)-(Mathematical formula 5) When the flow rate Q is fixed, the number of rotations is constant (angular velocity ω-fixed). The efficiency η is determined by the static pressure change Δδ from the upstream side to the downstream side, which represents the speed change AV2, and the torque T of the cross-flow fan. In the performance evaluation of Figure 6 <, the flow rate and the number of rotations are constant. Regardless of the blade shape, the pressure surface is the same, the maximum thickness 値 is fixed, and the outer diameter and the minimum inner diameter of the blade are fixed. The given conditions for the ratio of inside and outside diameter are given. The changing state of the outer periphery of the blade in the direction of the rotation axis is a shape shown in Fig. 4 (f) which changes linearly. It is a condition given D! ≪ D2. In all the conditions, from D! To D 2 The rate of change is equal. Therefore, according to Fig. 6, the radius of curvature is used as a parameter to evaluate the air-supply performance, and it is judged that the negative areas where the curvature radii of two arcs in which the center line 17 of the blade cross-sectional shape is formed are mutually inverted are the maximum efficiency points. That is to say, the curved and inverted shape of the outer front end of the blades 12 will have the effect of improving the performance of the cross flow fan 1, and will help improve the performance of the air conditioner. In Fig. 4 (e), the cross-sections of the two blades 12 depicted are cross-sections at arbitrary positions in the direction of the rotation axis, and the positions are shown in a cross-sectional view of a block viewed from the semi-controlling direction (f). . The thicker and larger section A indicates the side of the circular plate 3 of a fan block, and the thinner and smaller section A indicates the opposite side. From the cross-sectional view, it can be seen that the pressure surface 18 is substantially uniform with respect to the direction of the rotation axis. In (f), the change of the outer diameter with respect to the direction of the rotation axis changes linearly from the diameter D! To the diameter D2. The reason for the relationship is D! # D2 is used to add the Blade (10) 1227763 The effect of sound reduction. Generally, the portion of the pressure surface of the blade of the blower is an area where the fluid is directly powered, and it has a great influence on the performance of the blower. If the pressure surface is skewed, the fluid balance will be poor and uneven flow will be strong, resulting in problems such as reduced performance and increased noise. This kind of problem is caused by the above-mentioned fluid properties, which can basically be solved by the same principle. The contents are described below. Judging from the mathematical expressions (1) and (2) described earlier, noise and input will be greatly affected by the representative speed V. Therefore, the larger the flow velocity V, the more the noise will increase and the input will increase. This is a velocity distribution focusing on the rotation axis direction of the fluid flowing between the blades. When the pressure surface is skewed in the direction of the rotation axis, its shape is the main reason, and the speed distribution will greatly change in the direction of the rotation axis. Conversely, when the pressure surface is the same for the direction of the rotation axis, the velocity distribution will be approximately uniform, and the fluid will flow out at the same flow rate. At this time, the traffic is regarded as constant to compare the speed distribution of the two sides, and the impact on performance will be described below. For blades with a skewed pressure surface, compared to the flat and average flow velocity Vave calculated from the flow, there are areas where the local flow velocity V is fast and slow. The input of each small area of the speed distribution will be large in the area where the speed is fast. It will be small in low speed areas. As shown in Mathematical Formula (2), the input is increased by the quadratic of the flow velocity, and its velocity distribution. The increase in the high-speed region is more than that in the low-speed region. As a result, the total input It is larger than the input of the uniform velocity distribution of the whole. In other words, the blades with the same pressure surface will have approximately the same velocity (vave) as compared to the average velocity vave calculated from the flow rate. It can also be said that the minimum velocity input is -16- (11) 1227763. Even from the perspective of noise, as shown in Mathematical Formula (1), blades with a skewed pressure surface will increase the noise due to the existence of a region with a high velocity v, while blades with a uniform pressure surface will become the lowest speed of noise. distributed. From the point of view of speed distribution, the speed distribution of a piece with the same pressure surface in the direction of the rotation axis will be the same, and the input and noise will be in the best state. Therefore, as described above, by setting the pressure surface 18 to the direction of the rotation axis, the fluid balance can be improved, the air supply performance can be improved, and the silence can be achieved. By limiting the flow path width of the blade, performance can be improved, and its content is illustrated in Figure 5. The inter-blade flow path width B shown in (g) is the maximum width Bmax on the blade inner diameter side and the minimum width BmiN on the blade outer diameter side. The maximum width B ma X 'is expressed as Bmax = r * iNsiN0, and the minimum width BmiN is determined by using the blade inner diameter ri N shown in (h), the blade inner diameter front end, and the rotation axis as the base point. It is defined as the minimum width on the outer diameter side of the blade. In this state, Fig. 7 shows the effect of evaluating the fan performance using only the change ratio BmiN / Bmax of the flow path width 1 as a parameter. The maximum thickness of the blade is fixed, and the inner diameter and outer diameter of the blade are also fixed to give a certain condition of the ratio of the inner diameter to the outer diameter. The two ends of the inner diameter and outer diameter of the blade are also made equal to each other (also R). To compare. The efficiency η is the same as the above-mentioned fan efficiency η for a cross-flow fan that does not have the air-supply performance. The pressure change and flow amount from the upstream side to the downstream side of the cross-flow fan are incorrectly given by the torque and the number of rotations given by the fan. The decision. Here, the relationship between the efficiency η and the change ratio of the flow path finding degree to half BmiN / Bmax will be described. Near the outlet of the cross-flow fan, the flow Q is constant, so -17- (12) 1227763
BmiN/Bmax越小則通過流路寬度BmiN的流體速度會變的越 大。 可是，流體的性質上，流體速度越大則各流體區域的 損失也會變大，在橫流風扇的下流側，流速會下降到對應 於流量Q的速度分布。藉由橫流風扇來施加扭力T而過 分增加速度的流體，不會使靜壓力P s上升而損失的能量 會增加。結果，在流路寬度變化比率BmiN/Bmax爲55%以 下的區域，由於流路寬度B m iN變狹窄而讓效率變差。而 馨The smaller BmiN / Bmax, the greater the fluid velocity through the flow path width BmiN. However, in the nature of the fluid, the larger the fluid velocity is, the larger the loss of each fluid region becomes. On the downstream side of the cross flow fan, the velocity decreases to a velocity distribution corresponding to the flow rate Q. A fluid whose speed is excessively increased by applying a torsional force T by a cross flow fan will not increase the static pressure P s and increase the energy lost. As a result, in a region where the flow path width change ratio BmiN / Bmax is 55% or less, the flow path width B m iN becomes narrower and the efficiency deteriorates. While Xin
在BmiN/Bmax很大的區域，是與很小的情況相反’通過流 路寬度BmiN的流體速度會變小。因此，在橫流風扇吹出 口流體並不會增加很多速度而流出。在該狀態下，即使在 橫流風扇施加扭力T，靜壓Ps、動壓Pd不會一起上升而 讓流體通過橫流風扇。結果，在流路寬度變化比率 B m i N / B m a X爲8 5 %以上的區域，效率比η / η m a x會顯示較低 的値，效率會變差。而在流路寬度變化比率BmiN/Bmax爲 6 0〜8 0 %的區域，由於靜壓P s、動壓P d、扭力T的平衡 I 性很好’所以效率比η/ηηΊαχ會顯示較高的値。由以上可得 知，在風扇的葉片間流路寬度外徑側對於內徑側爲6 0〜 8 0 %的區域效率較高可提升風扇的性能。當於室內單元搭 載上述構造範圍的橫流風扇來進行運轉時，能夠以相同的、 消耗電力來使風量增加’而可提升空調機全體的性能。 以上’是用以等間隔來形成葉片間間隔的橫流風扇來 加以說明’可是即使是不等間隔的橫流風扇也可以使用這 種想法。以下’來加以說明。現今內裝於空調機的室內單 -18- (13). 1227763 / 元的橫流風扇，相對於圓周方向是以不等間隔來配置葉片 的構造較多。也就是’橫流風扇的各葉片之間的BmiN、 B m a X是不相等的’各流路寬度也並不相等。這是爲了要應 用上述的習知技術，藉由使葉片的相位錯開而具有能將橫 流風^旋轉時的干涉所造成的葉片聲音減低的效果，是被 廣泛使用在現在的空調機的室內，單元。因此關於葉片間隔 不同的橫流風扇’上述的流路寬度變化比率BmiN/Bmax是 顯示在各葉片間不同的値。因此，對於以上的葉片間隔不 同的橫流風扇，是使用爲了決定流路寬度變化比率 BmiN/Bmax而被平均化的數値。當在一個橫流風扇區塊的 圓周方向是以不等間隔配置有N片葉片時，Bmax = riNsiN (2π/Ν ) ，BmiN= ( ΣΒ’11ΊΐΝ ) /Ν。Bmax 是從藉由葉片片數 N來將橫流風扇的一周平均化的角度來計算出來的，BmiN ，則是當將橫流風扇的各葉片間的最小f路寬度當作 B’miN時，藉由葉片片數 N來將全部葉片間的總和（ ΣΒ’ηιίΝ )平均而求出來的。藉此’在不等間隔的橫流風扇 就可決定流路寬度變化比率BmiN/Bmax。 上述流路寬度的調整’基本上藉由調整葉片的厚度則 可加以對應。即使葉片的間隔相等只要之前的流路寬度變 化比率BmiN/Bmax爲60〜80%的話，將任何葉片（一片以 上的葉片）的厚度作成與其他葉片的厚度不同也可以（全 部的葉片不是相同厚度也可以），即使是不等的間隔，而 只要平均値在該値內的，即使全部的葉片厚度不相同也可 以。 -19- (14) 1227763 在第8圖顯示了以往的風扇與本實施風扇的性能比較 。橫軸爲風量比Q/Q〇，縱軸則分別爲：全壓比PT/PTo， 輸入比L m / L m 〇 ’噪音値s L - S L 〇。這裡的Q ο、Ρ Τ 〇、L m 〇 、SL〇是表示以往的基準値。條件爲相同轉數，以往的風 扇的型態是與本實施風扇同樣的內外徑，因此內外徑比也 相等。而對於旋轉軸方向葉片外徑會變化，在一個風扇區 塊的軸方向的中間位置附近是直線性地變化成最大外徑。 這具備有本實施例也使用的抑制葉片聲音的效果，其他的 _ 葉片間流路寬度變化爲6 0〜8 0 %，兩圓弧並不是使反轉、 壓力面一致的形狀。如第8圖所示，比較各風量比的話， 全壓比約爲+20%，輸入比約爲—10%，噪音値約爲—ldB ’則很明顯藉由本實施例改善了性能與噪音。 【發明效果】 藉由本發明，藉由使橫流風扇高效率、低噪音化，貝ij 能夠提供使風量增加且減低噪音，節省電力且安靜的空調 # 機。 【圖式簡單說明】 第1圖是顯示本發明的一實施例方式的全體圖。 第2圖是上述一實施型態的橫流風扇圖。 第3圖是上述一實施型態的葉片剖面放大圖。 第4圖是上述一實施例型態的葉片剖面放大圖，風扇 區塊剖面圖。 -20- (15) 1227763 第5圖是上述一實施例型態的葉片剖面放大圖，風扇 區塊剖面放大圖。 第6圖是顯示上述一實施例型態的效果的效率圖。 第7圖是顯示上述一實施例型態的效果的效率圖。 第8圖是顯示上述的一實施例型態的性能的特性圖。 【圖號說明】 1 :橫流風扇 2 :裝飾框 3 :前面格柵 4 :上面格概 5 :過濾器 6 :熱交換器 7 :殼體 8 :縱風向板 9 :橫風向板 β 1 〇 :馬達 1 1 :筒口 12 :葉片 1 3 :圓板 1 4 :端面圓板 1 5 :轂部端面圓板 1 6 :轂部 17 :彎曲線 -21 - (16)1227763 1 8 :壓力面In a region where BmiN / Bmax is large, it is the opposite of a small case. 'The fluid velocity through the flow path width BmiN becomes smaller. Therefore, the fluid does not flow out at a high speed at the outlet of the cross flow fan. In this state, even if the torsional force T is applied to the cross-flow fan, the static pressure Ps and the dynamic pressure Pd do not rise together, and the fluid passes through the cross-flow fan. As a result, in a region where the flow path width change ratio B m i N / B m a X is 85% or more, the efficiency ratio η / η m a x shows a lower 値, and the efficiency deteriorates. In the area where the flow path width change ratio BmiN / Bmax is 60 to 80%, the static pressure P s, the dynamic pressure P d, and the torque T are well balanced, so the efficiency ratio η / ηηΊαχ will be higher.値. From the above, it can be known that the efficiency of the fan can be improved in a region where the outer diameter side of the flow path width between the blades of the fan is 60% to 80% on the inner diameter side, and the efficiency is higher. When the indoor unit is operated with a cross flow fan having the above-mentioned structural range, the same amount of power can be used to increase the air volume ', and the performance of the entire air conditioner can be improved. In the above, "the cross-flow fan for forming the space between the blades at equal intervals has been described", but even the cross-flow fan with unequal intervals can use this idea. This is explained below. Today's indoor units installed in air conditioners are -18- (13). The 1227763 / yuan cross-flow fan has many structures with blades arranged at unequal intervals in the circumferential direction. In other words, 'BmiN and B m a X between the blades of the cross flow fan are not equal' and the widths of the flow paths are not equal. This is to apply the above-mentioned conventional technology, and by shifting the phase of the blades, it has the effect of reducing the blade sound caused by interference when the cross-flow wind ^ is rotated. It is widely used in the indoors of current air conditioners. unit. Therefore, the above-mentioned flow path width change ratio BmiN / Bmax for the cross-flow fans having different blade intervals is shown to be different between blades. Therefore, for the above-mentioned cross-flow fans having different blade intervals, the number averaged in order to determine the flow path width change ratio BmiN / Bmax is used. When N blades are arranged at unequal intervals in the circumferential direction of a cross-flow fan block, Bmax = riNsiN (2π / N), and BmiN = (ΣB'11ΊΐN) / N. Bmax is calculated from the angle of averaging one cycle of the cross-flow fan by the number of blades N. BmiN is when the minimum f-path width between the blades of the cross-flow fan is taken as B'miN. The number of blades N is calculated by averaging the sum (ΣΒ'ηιίΝ) between all the leaves. With this, the cross-flow fans at unequal intervals can determine the flow path width change ratio BmiN / Bmax. The above-mentioned adjustment of the flow path width can basically be adjusted by adjusting the blade thickness. Even if the intervals between the blades are equal, as long as the previous flow path width change ratio BmiN / Bmax is 60 to 80%, the thickness of any blade (more than one blade) can be made different from the thickness of other blades (all blades are not the same thickness) (Also), even at unequal intervals, as long as the average 値 is within the 値, even if all the blade thicknesses are different. -19- (14) 1227763 Figure 8 shows the performance comparison between the conventional fan and the fan of this embodiment. The horizontal axis is the air volume ratio Q / Q0, and the vertical axis is the full pressure ratio PT / PTo, the input ratio L m / L m 〇 'noise 値 s L-S L 〇. Here, Q ο, PT 〇, L m 〇, and SL 〇 are conventional reference values 表示. The conditions are the same number of revolutions, and the conventional fan has the same inside and outside diameter as the fan of this embodiment, so the inside and outside diameter ratios are also equal. On the other hand, the outer diameter of the blade changes in the direction of the rotation axis, and it changes linearly to the maximum outer diameter near the middle position in the axial direction of one fan block. This has the effect of suppressing the blade sound also used in this embodiment. The other _ the change in the width of the flow path between the blades is 60 to 80%, and the two arcs are not shapes that make the inversion and the pressure surface consistent. As shown in FIG. 8, when comparing the various air volume ratios, the total pressure ratio is approximately + 20%, the input ratio is approximately -10%, and the noise is approximately -ldB ′. It is obvious that the performance and noise are improved by this embodiment. [Effects of the Invention] With the present invention, by making the cross-flow fan highly efficient and reducing noise, Beij can provide an air-conditioning machine that can increase air volume, reduce noise, save electricity, and be quiet. [Brief Description of the Drawings] Fig. 1 is an overall view showing an embodiment of the present invention. Fig. 2 is a cross-flow fan diagram of the embodiment. Fig. 3 is an enlarged sectional view of a blade according to the embodiment. Fig. 4 is an enlarged sectional view of a blade and a sectional view of a fan block according to the embodiment. -20- (15) 1227763 Fig. 5 is an enlarged sectional view of a blade and an enlarged sectional view of a fan block according to the above embodiment. FIG. 6 is an efficiency diagram showing the effects of the embodiment type. FIG. 7 is an efficiency diagram showing the effect of the embodiment type. FIG. 8 is a characteristic diagram showing the performance of the above-mentioned embodiment. [Illustration of drawing number] 1: Cross flow fan 2: Decorative frame 3: Front grille 4: Upper grid 5: Filter 6: Heat exchanger 7: Case 8: Cross wind direction plate 9: Cross wind direction plate β 1 〇: Motor 1 1: Cone 12: Blade 1 3: Circular plate 1 4: End face circular plate 15: Hub end face circular plate 1 6: Hub 17: Bending line -21-(16) 1227763 1 8: Pressure surface
-22--twenty two-