1270635 ⑴ 九、發明說明 【發明所屬之技術領域】 本發明係關於一體型空調機。 【先前技術】 一般而言，一體型空調機，係自機組前面吸入空氣， 經由室內側熱交換器，使空氣到達室內風扇的吸入口側。 Φ 在室內風扇的吸入口側，在其周圍，設有設置在殼上的口 環。在通風路利用室內熱交換器冷卻後的空氣，自室內風 扇的周圍吹出，而構成可以自機組前面向室內吹出。 被記載於專利文獻1中的一體型空調機，係在機組的 則面’設置空氣吸入口’並在其左右兩邊，設置空氣吹出 口。而且，自室內風扇吐出的空氣’係自設置在機組裝飾 框的左右兩邊的吹出口，向機組外吹出。殻係被構成，使 得自左右兩邊的吹出口吹出的風量，可以左右兩邊相等。 具體而固’利用在室內風扇的左下方和右上方設置凸形的 鼻錐，謀求吹出風量的均等化。 又，離心式風扇的構造，如專利文獻2所記載，係由 輪轂；被直立設置在輪轂上的複數個輪葉；及覆蓋輪轂的 另一側的輪葉的外周，並形成吸入口的覆緣所構成；並作 成相對於覆緣內徑，與輪轂連接的輪葉外徑較大的構造。 【專利文獻1】日本特開2 00 1 -22 1 45 7號公報 【專利文獻2】日本特開2002-61597號公報 (2) 1270635 * 【發明內容】 (發明所欲解決之課題） 然而，專利文獻1所記載的一體型空調機，會發生原 因尙未完全明瞭的碑體音’會有在機組前面的噪音變高之 類的問題。 又，室外風扇，在被設置成自機組的周圍吸入的空氣 ，由吸入口吹向設置在其軸方向的下游側之室外熱交換器 ^ 的構成之情況，會發生流體音’而有機組噪音變大的問題 。因此，由於要增加輪葉所做的功量’所以要增加驅動風 扇所需要的動力。因而，風扇馬達的輸入電力變高，會有 機組的消耗電力增加的問題。 本發明的第1目的在於：針對在室內熱交換器的下游 側，經由口環，配置離心式室內風扇而成的一體型空調機 ，降低其噪音。 又，第2目的在於提供一種一體型空調機，針對在室 φ 外風扇的下游側配置室外熱交換器而成的空調機，降低其 噪音和風扇馬達輸入。 又，第3目的在於提供一種提局室內風扇的風扇效率 之一體型空調機。 (解決課題所用的手段） 前述第1目的係藉由以下的一體型空調機來達成，亦 即針對在機組內收容壓縮機、室外熱父換器、室內熱父換 器、室內風扇及室外風扇之/體型空調機’其特徵爲具備 -6 - 12706351270635 (1) Description of the Invention [Technical Field of the Invention] The present invention relates to an integrated air conditioner. [Prior Art] In general, an integrated air conditioner draws air from the front of the unit and passes the indoor side heat exchanger to allow air to reach the suction port side of the indoor fan. Φ On the suction side of the indoor fan, a ring provided on the case is provided around it. The air cooled by the indoor heat exchanger in the air passage is blown out from the periphery of the indoor fan, and the air blows from the front of the unit to the inside of the room. The integrated air conditioner disclosed in Patent Document 1 is provided with an air intake port on the front surface of the unit, and an air blowing port is provided on the left and right sides thereof. Further, the air ejected from the indoor fan is blown out from the outside of the unit from the air outlets provided on the left and right sides of the frame of the unit. The shell system is constructed such that the amount of air blown from the air outlets on the left and right sides can be equal to the left and right sides. Specifically, a convex nose cone is provided on the lower left and right upper sides of the indoor fan, and the amount of blown air is equalized. Further, the structure of the centrifugal fan is as described in Patent Document 2, which is a hub; a plurality of vanes which are erected on the hub; and an outer circumference of the vane covering the other side of the hub, and which forms a suction port. The rim is configured; and the outer diameter of the vane connected to the hub is large with respect to the inner diameter of the rim. [Patent Document 1] Japanese Patent Laid-Open Publication No. JP-A-2002-61597 (Patent Document 2) Japanese Laid-Open Patent Publication No. 2002-61597 (2) 1270635 * SUMMARY OF INVENTION [Problems to be Solved by the Invention] However, In the integrated air conditioner described in Patent Document 1, there is a problem that the noise of the monument is not completely understood, and there is a problem that the noise in front of the unit becomes high. In addition, in the outdoor fan, when the air sucked in from the periphery of the unit is blown toward the outdoor heat exchanger provided on the downstream side in the axial direction, the fluid sound is generated and the organic group noise is generated. Bigger problem. Therefore, the power required to drive the fan is increased because of the amount of work done by the vanes. Therefore, the input power of the fan motor becomes high, and there is a problem that the power consumption of the unit increases. A first object of the present invention is to reduce the noise of an integrated air conditioner in which a centrifugal indoor fan is disposed via a port ring on the downstream side of the indoor heat exchanger. Further, a second object of the invention is to provide an integrated air conditioner that reduces the noise and the fan motor input to an air conditioner in which an outdoor heat exchanger is disposed on the downstream side of the outer fan of the chamber φ. Further, a third object is to provide a body type air conditioner which is a fan efficiency of an indoor fan. (Means for Solving the Problem) The first object is achieved by the following integrated air conditioner, that is, the compressor, the outdoor hot parent converter, the indoor hot parent converter, the indoor fan, and the outdoor fan are housed in the unit. / body type air conditioner 'characterized by having -6 - 1270635
口環，其被設置在前述室內風扇或室外風扇的吸入口 的周圍；及 板狀構件’其被設置在此室內風扇或室外風扇的吸入 口外周的一部分或是全部，並具有比此口環的隆起高度更 高的部分。 前述第2目的係藉由以下的一體型空調機來達成，亦 即針對在機組內收容熱交換器；及離心式風扇，此風扇將 複數個輪葉配置在其輪轂上，並將覆緣設置在此輪葉的輪 轂側的另一側之一體型空調機，其特徵爲： 具備：與被設置在前述離心式風扇的軸方向之熱交換 器一起形成吐出空間之間隔板；及被設置在此間隔板上， 形成前述離心式風扇的吸入口之口環； 並將前述離心式風扇，使其連接前述輪轂之輪葉外徑 ，比前述覆緣吸入口的內徑小。 前述第3目的，係藉由以下的一體型空調機來達成， 亦即針對在機組內收容壓縮機；室外熱交換器；室內熱交 換器；離心式室內風扇，此風扇將複數個輪葉配置在其輪 轂上，並將覆緣設置在此輪葉的輪轂側的另一側；及室外 風扇之形態的一體型空調機，其特徵爲： 將前述室內風扇，使其連接前述輪轂之輪葉外徑，比 前述覆緣吸入口的內徑大。 【實施方式】 -7- (4) (4)1270635 (實施發明的最佳形態） 以下，根據第1圖〜第6圖來說明本發明的一實施例 〇 第2圖係表示關於本實施例的一體型空調機1 00的平 面圖。一體型空調機100，在其框體101的內部，設置用 來將其區分成室內側和室外側之間隔板1 02。在室內側， 配設熱交換器103、及吸入室內空氣來促進熱交換器103 的熱交換之離心式的室內風扇10;並設置用來將自室內風 扇10吐出的空氣，導流至被設置在一體型空調機100的 前面左右兩邊的吹出口 104之風路20。此風路20的前面 側，係在熱交換器1 03和室內風扇1 0之間，藉由吸入側 殻21來構成；背面側則藉由背面側殻1 9來構成。口環1 ，被配置在吸入側殼2 1的室內熱交換器1 03側的面上。 在口環1的風路20側，配置自軸方向吸入空氣，再往周 圍方向吹出的離心式室內風扇1〇。自室內風扇10往一體 型空調機1〇〇的寬度方向吐出的空氣，爲了使其自前面向 室內吹出，而被轉向9 0度。 在風路2 0中，以將室內風扇1 0所吐出的空氣往左右 分配爲目的，如第4圖的正面剖面圖所示，設置突起狀的 鼻錐2 2、2 3。 又，回到第2圖，如第1圖所示的構成之吸入環2， 被裝設在口環1的外周。 在室外側，設置壓縮機1 〇 5、熱交換器1 0 6及離心式 的室外風扇3 0，此室外風扇3 0係自設置在框體的左右側 (5) 1270635 _ 面和頂面之外氣取入口 1 07吸入外氣，來促進熱交換器 1 〇 6的熱交換。室內和室外風扇係被連結至風扇馬達1 〇 8 ，藉由風扇馬達1 0 8旋轉，兩風扇旋轉。 壓縮機105、室內熱交換器103及室外熱交換器1〇6 ，利用冷媒配管連結起來，構成一相連的冷凍循環。 一體型空調機1 〇〇，並被構成結露水流路（未圖示） ，當冷氣運轉時，使得在室內熱交換器1 〇 3所產生的結露 φ 水，可以流出至室外側的框體底部。 如第1 1圖所示的飛濺環3 5，被設置在室外風扇3 0的 外周；揚起貯存在室外側的框體底部之結露水，產生霧狀 的水滴而噴向室外熱交換器106，使室外熱交換器106的 能力提高。 接著，根據第1圖來說明將本發明的一實施例亦即吸 入環2適用於室內風扇1 0的例子。口環1，係被設置在收 容離心式室內風扇1 0之風路20的吸入口側的吸入側殻2 1 φ 上。口環1的其中一端，被安裝在吸入側殻2 1上，另一 端則被插入室內風扇1 0的覆緣1 1的吸入口。將板形成圓 弧狀的吸入環2，被裝設在口環1的外周。吸入環2，不 需要覆蓋口環1的整個外周，也不一定要如本實施例般的 C型板狀（半圓弧的板狀肋），也可以將沒有彎曲部的板 狀構件（肋）設置在口環1的外周。本實施例係將圓弧狀 的吸入環2設置在口環1的上方半圓部分的例子。又，吸 入環2，也可以作成與口環1分開的另外的零件，而裝設 在風路2 0的吸入側殼21上；也可以使用與口環1 一體成 -9- (6) (6)1270635 形者。 吸入環2的設置位置，理想爲位於口環1的外形（外 表）MD2以上（比外形MD2更外側）。吸入環2，至少需 要被直立設置在風路2 0上部的被形成凸形的鼻錐2 2和風 路2 0下部之被形成凸形的鼻錐23的範圍中之自鼻錐22 往室內風扇1 〇的旋轉方向至鼻錐23的範圍。 又，吸入環2的高度SH，理想爲比口環1之自吸入 側殻2 1的面算起的高度MH大。不需要全部比口環1的 隆起高度大，只要使噪音降低最有效之處增高便足夠。 就前述構造的一體型空調機而言，說明室內風扇1〇 的作用。 在習知的室內風扇的吸入口側，並沒有設置吸入環2 。因此，會產生原因不明的噪音。目前爲止，雖然尙未完 全詳細地瞭解噪音產生的機構，但是根據空氣流的可視化 實驗等，已經得到一個有力的學說。以下，加以說明。 如第2圖所示，室內風扇1 〇的軸中心，係從一體型 空調機1 00的橫向寬度的中心偏離。這是因爲收容壓縮機 1 〇5的關係，想要使室內風扇的軸中心遠離收容壓縮機 1 〇5的空間而使其錯開。爲了使設置在本體的正面左右兩 邊的吹出口 1 04的吹出風量相同，如第4圖所示，以此來 決定鼻錐22、23的形狀和高度等。由於在風路20的左右 兩邊的鼻錐的高度相異，所以自室內風扇1 0吹出的空氣 的通過剖面積也左右相異；在相同量的空氣往殻的左右兩 邊流動的情況，通過剖面積小的其中一側，其流速變快， -10- (7) (7)1270635 靜壓降低。由於此種原因，自室內風扇1 〇吐出的氣流速 度，在殻的左右兩邊，會發生差異。若在風路20的左右 兩邊，氣流速度發生差異，則通過口環1的空氣，會被其 氣流速度快而變成低壓的風路2 0側所吸引，而會產生相 對於被吸入室內風扇1 〇的吸入口的中心部的氣流之流動 ，於是在風扇吸入口處，氣流紊亂。由於此紊亂的氣流（ 亂流）而發生流體音，被認爲將會使機組前面的噪音變高 。進而，使用第1、4、5圖，詳細地說明。 如第1圖所示’藉由離心式室內風扇1 0被旋轉驅動 ，室內的空氣，通過室內熱交換器103而被吸入口環1內 。此時，與自軸方向來的主流同時，自口環1的口徑MD! 的外周方向被吸入的空氣，沿著風路20的壁面2 1的表面 ，進而沿著往風扇軸方向隆起的形狀的口環1的表面，被 吸入室內風扇1 〇。 如第4圖的一體型空調機正面圖所示，藉由室內風扇 1 0的旋轉而往離心方向吐出的空氣，會被分配至風路2 0 的左右兩邊。在風路20中，爲了使自離心式室內風扇10 的周圍方向吐出的空氣’有效率地分配至左右兩邊，設置 突起狀的鼻錐22、23。風路20的鼻錐23側的剖面積Al ，相對於鼻錐2 2側的剖面積A 2，係表示出A i < A 2的情況 的例子。將鼻錐2 3側的流速設爲v】、將鼻錐2 2側的流速 設爲v2，並將室內風扇1〇往左右的風路20吐出的風量q 設爲相同。此時，流速v和風量Q、剖面積A的關係爲 v = Q / A ,所以v 1〉v 2。在風路2 0的左右兩邊’右空氣的流 -11 - (8) 1270635 速分佈相異，則流速快的鼻錐23側，相對於鼻錐22側， 其靜壓變低。由於空氣容易往壓力較低的一方流動，所以 沿著口環壁面流動的空氣，會被引入鼻錐23側。 使用第5圖來說明此情況。第5圖係自室內熱交換器 側來看被口環1包圍的吸入口的斜視圖；是表示口環1的 表面的空氣的流動的圖。面向紙面，左邊的圖是沒有設置 吸入環2的圖，右邊的圖則是設有關於本實施例的吸入環 φ 2的圖。如左圖所示，沒有吸入環2的情況，相對於室內 風扇1 〇的旋轉，鼻錐2 3側的空氣2 0 0，在被吸入靜壓低 的風路2 0內的時候，被認爲會被形成抗拒室內風扇1 〇的 旋轉之氣流。如此’若在風扇吸入口發生與要被吸入室內 風扇1 〇的中心部的氣流相對之氣流，則氣流會紊亂；結 果’成爲流體音發生的原因，而被認爲是招致噪音增加的 原因。 相對於前述所示的空氣的流動，根據第5圖的右圖來 φ 說明設置吸入環2的情況的作用。 _ 若將吸入環2裝設在口環1的外周，自室內吸入的空 氣沿著吸入側殻2 1的壁面表面被吸入口環1內的時候， 會衝撞吸入環2，暫且以氣流速度降低的狀態，經由口環 1而被導引至室內風扇1 〇的吸入口。如本實施例所示，利 用將吸入環2半圓狀地設置在口環1的上方側（自流速會 變快的風路2 0的鼻錐2 2直到鼻錐2 3的圓弧狀），在室 內風扇1 0的吸入口處，通過吸入環2的空氣的氣流速度 會降低。由於室內風扇1 〇逆時針旋轉，本實施例的室內 -12- (9) 1270635 風扇1 0 ’在第4圖中，係往逆時針方向旋轉，而根據風路 20的鼻錐22和鼻錐23的位置關係，在被吸入環2覆蓋的 離心式室內風扇1 0的上方側所吸入的空氣的大部分，會 流向鼻錐23側的風路2〇。因此，利用藉由吸入環2來抑 制自周圍方向沿著表面被吸入的氣流的速度，抑制鼻錐23 側的風量’變成v! 4 V2的關係，殻內的左右兩邊的靜壓變 成大約相等。如第5圖的右圖所示，沿著口環壁面表面流 φ 動的空氣，會流向室內風扇1 〇的中心部，風向被統一成 相同方向而沒有亂流。 如此’利用減少由於亂流所產生的流體音，室內側的 噪音降低。前述的學說爲假說，由於實際上能否謀求噪音 降低尙不明朗，所以將實際上有無吸入環2的情況之室內 側的噪音比較資料表示於第6圖。若以相同風量來比較， 有吸入環2的一方，噪音値大約低i d b。根據此結果可知 ’利用將吸入環2裝設在一體型空調機丨〇 〇的室內風扇1 〇 φ 用的口環1上，能夠得到降低室內側的噪音的效果。 前述吸入環的構造，只要是第4圖所示的風路2 0和 室內風扇10的構成，若至少自鼻錐22往逆時針方向在鼻 錐的範圍內，帽簷狀地被設置（被設置在設有鼻錐的風路 的裏面），則會給予抑制在室內風扇的吸入口處的亂流之 作用，氣流音被減少，所以可以得到室內側的噪音降低的 效果。 再者，在本實施例中，係說明了關於設有二個室內側 的吹出口之一體型空調機’但是即使是一個吹出口，當空 -13- (10) 1270635 氣的流速快時，與前述同樣的，自風扇周圍方向沿著口環 的表面被吸入風扇的空氣流之中，仍會有抗拒風扇旋轉方 向的氣流流入，而產生噪音的情況。又，吹出口爲三個以 上（除了正面的左右兩邊以外，加上在正面的下部設置吹 出口的情況），也預料將會產生流速快的風路，此情況也 是成爲噪音發生的原因。如此的情況，關於本實施例的吸 入環也是有效的。 接著，使用第7圖來說明吸入環2的變化例。 藉由吸入環所產生的室內噪音的降低效果，即使是第 7圖所示的口環3的情況，也可以得到同樣的效果。第7 圖的口環3，係遮斷氣流的流動的形狀，並將圓弧狀的肋 4 一體地射出成形在口環壁面表面上而成者。肋4，在如 第4圖所示的往逆時針方向旋轉的室內風扇1 〇的情況， 只要帽簷狀地至少被設置在自鼻錐2 2往逆時針方向至鼻 錐2 3的範圍內便可以。本實施例的肋4，係成爲與吸入環 2相同的覆蓋風扇吸入口的C字型的形狀。藉由此肋4， 抑制流入風扇吸入口的空氣的速度，而可以調節風路20 內部的左右二邊的氣流速度；結果，與吸入環2的作用相 同’可以抑制在風扇吸入口處的亂流，而能夠得到室內噪 首的降低效果。 再者，前述實施例中，皆是作成圓弧狀的肋形狀的吸 入環2 ’但是爲了降低第5圖的左圖所示的表面氣流2 0 0 的流速’在此氣流的上游，設置直線的板狀肋，相較於第 5圖的右圖，能夠謀求噪音降低。 •14- (11) 1270635 接著，使用第8圖來說明室外風扇30的一實施例。 第8圖所示的一體型空調機丨〇 〇，係將吸入環2適用 在室外風扇3 0的口環5上的例子。室外側，藉由室外風 扇3 0的驅動，自外氣取入口〗〇7吸入空氣，通過固定在 風扇蓋110上的口環5，而被吸入室外風扇30，再使自室 外風扇吐出的空氣，吹向室外熱交換器106而放出至室外 。在本實施例中，係表示適用L字形的熱交換器的例子； g 如此’由於在室外風扇30的吐出口左右兩邊，空氣的通 過剖面積相異，所以自風扇吐出的氣流速度相異。如前所 述’由於風扇吸入口的空氣會被吸入氣流速度快的低壓側 ’所以相對於被吸入風扇中心部的氣流，產生氣流的紊亂 ’而發生流體音。此流體音會往室外側洩漏而增加室外噪 音。 利用將第1圖所示的吸入環2裝設在口環5的外周， 通過吸入環2的氣流速度降低，抑制室外風扇3 0的左右 φ 兩邊的吐出氣流的速度差，而利用自室外風扇3 0至室內 熱交換器1 03的空間內的靜壓分佈，沿著口環5壁面流動 的空氣，會流向室外風扇3 0的中心部，風向被統一成相 同的方向，氣流的紊亂消失。結果，能夠去除由於氣流的 紊亂所產生的流體音的發生，而由於洩漏至室外的噪音， 並沒有流體音的加入，所以室外噪音降低。 又，室外風扇3 0沒有使用吸入環2的情況’也可以 如第7圖所示的口環3，設置設有肋4之口環。 第1圖所示的吸入環2或第7圖所示的口環3的適用 -15- (12) 1270635 方法，如以下的三種。（1 )僅適用在室內側的風扇。（2 )分別適用在室內側和室外側的風扇。（3 )僅適用在室 外側的風扇。 接著，使用附有室內外的風扇的形狀之第9圖〜第1 1 圖來說明。 在第9圖中，室內風扇10係由：在旋轉中心部，具 有用來傳遞風扇馬達1 0 8的旋轉力的軸套1 2之輪轂1 3 ; 以一定的間隔被配置在輪轂1 3上之複數個輪葉1 4 ;及在 輪轂1 3的相反側，與各輪葉1 4連結之覆緣1 1所構成。 輪葉14的外徑D2，相對於覆緣1 1的最大外徑D2Sl，係 設成D2SLg D2 ;如圖所示，爲了使自覆緣1 1側朝向輪轂 1 3側吐出的流速分佈適當化，在途中，設置反曲點1 4 a。 再者，也可以不設置反曲點1 4 a，而作成其外徑自覆緣1 1 側朝向輪轂1 3側漸漸地變小的形狀。但是，輪轂1 3側的 輪葉外徑D2H，相對於覆緣1 1的吸入口內徑D i S，係 D2H>DiS ;相對於輪轂外徑DH，係D2H>DH。 在第1 0圖中，室外風扇3 0係由：在旋轉中心部，具 有用來傳遞來自風扇馬達1 0 8的旋轉力的軸套3 2之輪轂 3 3 ;以一定的間隔被配置在輪轂3 3上之複數個輪葉3 4 ; 及在輪轂3 3的相反側，與各輪葉34連結之覆緣3 1所構 成。輪葉34的外徑D2，相對於覆緣31的最大外徑D2Slj ，係設成D 2 s L 2 D 2 ;如圖所示，爲了使自覆緣3 1側朝向 輪轂3 3側吐出的流速分佈適當化，在途中，設置反曲點 3 4 a。也可以不設置反曲點3 4 a，而作成其外徑自覆緣3】 -16- (13) (13)1270635 側朝向輪轂3 3側漸漸地變小的形狀。但是’輪轂3 3側的 輪葉外徑D2H，相對於覆緣3 1的吸入口內徑D! S ’係 D 2 Η > D ! S ;相對於輪轂外徑D Η，係D 2 H = D Η。 室外風扇3 0，在裝設有用來揚起貯存在室外側框體底 部的結露水而噴向室外熱交換器1〇6之飛濺環35的本實 施例中，係表示將飛濺環3 5裝設在覆緣3 1外周的例子。 飛濺環35，係環狀地被設置在覆緣31外徑D2SL的外周 〇 一般的離心式風扇的構造，係如室內風扇1 〇那樣。 在本實施例中，室內風扇和室外風扇雖然皆是離心式風扇 ，卻使用相異輪葉形狀的風扇。 相對於室內風扇10係在吸入側設置熱交換器，室外 風扇3 0係在空氣吐出側設置熱交換器。亦即，吸入空間 和吐出空間係藉由風扇蓋（間隔板）1 1 0而被區隔，此吐 出空間，係被風扇蓋110和室外熱交換器106包圍（雖然 未圖示出來，上下方向係藉由頂板和底板來區隔成機組內 外）。而且，儘管是離心式的室外風扇30，室外熱交換器 1 〇 6也存在於此風扇的軸方向。因此，往風扇的直徑方向 被吐出的空氣，係被強制地往軸方向流動。再者，口環5 係被設置在間隔板亦即風扇蓋1 1 〇上，室外風扇3 0係被 配置成使此口環5成爲吸入口。詳細地說明此點。 室外風扇3 0，係自外氣取入口 1 〇 7經由口環5吸入空 氣。被風扇吸入的空氣，藉由風扇的旋轉，流過輪葉3 4 的壁面往而離心方向被吐出。自離心式室外風扇3 0吐出 -17- (14) (14)1270635 的空氣，由於要吹向室外熱交換器1 0 6，所以要變成吹向 軸方向。往軸方向吹，係藉由風扇蓋1 1 〇的形狀來決定風 向。因此，自覆緣3 1附近吐出的空氣，其風向會強制地 被改變成往軸方向。 在此，第9圖所示的離心式風扇構造的情況，輪轂側 的輪葉外徑D2H由於輪轂外徑大，所以若要將此風扇作爲 室外風扇30來適用時，室外風扇30吹出的空氣，若朝向 軸方向流動，則在輪轂側的輪葉面，由於使軸方向的流動 發生紊亂的功，所以會發生由於亂流所造成之伴隨著流體 音的室外噪音的增加、及伴隨著輪葉功量的增加而造成風 扇馬達108輸入的增加。 因此，將室外風扇3 0設爲第1 〇圖所示的室外風扇3 0 。亦即，此室外風扇3 0，由於輪轂側的輪葉外徑D2H和 輪轂外徑DH相等，相對於軸方向的流動，會成爲妨礙的 輪葉面積被縮小，由於能夠減少使軸方向的氣流發生紊亂 的原因，同時降低輪轂側的輪葉面的功量，所以謀求由於 流體音所造成的噪音的減少和馬達輸入的降低是可能的。 輪葉34的吐出口的高度b2和自覆緣3 1至反曲點34a 爲止的距離b3之間的關係，理想爲設成0.28<b3/b2<0.58 〇 將室外風扇的構造，從室內風扇1 0的形式變更成室 外風扇30的構造，並將b3/b2設爲=0.29，以相同風量使 用的情況，噪音大約降低3dB，馬達輸入則減少大約30% -18- (15) 1270635 室內風扇1 ο，由於將空氣往離心方向吐 悲、往室內吹出’所以若如室外風扇3 0那樣， 積裏、小’則空氣的吐出量會降低。比較室內丨 室內風扇10的構造變更成室外風扇30的構 能之結果’爲了要得到相同的風量，室外風 ’其旋轉數上升7.3 %，噪音則增加2 · 5 d B。 扇的旋轉數η和噪音SL的關係爲SL = 601og 以伴隨著旋轉數上升，會成爲噪音也上升的 室內風扇1 〇，其覆緣吸入口內徑D ! S和輪 d2H的關係，理想爲Dls<D2H。 以上’若根據本實施例，能夠提供一種 降低之一體型空調機。又，提供一種室外側 減少馬達輸入之一體型空調機。 [發明之效果] 以上，若根據本發明，針對在室內熱交 ，經由口環，配置離心式室內風扇而成的一 能夠降低其噪音。 又，能夠提供一種一體型空調機，針對 下游側配置室外熱交換器而成的空調機，降 扇馬達輸入。 又，能夠提供一種提高室內風扇的風扇 空調機。 再者，關於達成前述效果的作用，根據 出，並照此狀 輪葉14的面 風扇1 0、及將 造的風扇的性 扇構造的風扇 由於離心式風 (Πΐ/η2)，所 結果。因而， 轂側輪葉外徑 室內側的噪音 的噪音降低和 換器的下游側 體型空調機， 在室外風扇的 低其噪音和風 效率之一體型 前述的說明應 - 19- (16) (16)1270635 可明瞭。 【圖式簡單說明】 第1圖係表示吸入環的構造的圖。 第2圖係一體型空調機頂面剖面圖。 第3圖係一體型空調機剖面圖。 第4圖係一體型空調機正面剖面圖。 第5圖係表示口環周邊的風向的圖。 第6圖係表示吸入環的噪音降低效果的圖表。 第7圖係表示口環的構造的圖。 第8圖係一體型空調機頂面剖面圖。 第9圖係表示室內側離心式風扇的構造的剖面圖。 第1 〇圖係表示室外側離心式風扇的構造的剖面圖。 第1 1圖係表示室外側離心式風扇的構造的圖。 【主要元件符號說明】 1 : 口環 2 :吸入環 4 :肋 1 〇 :室內風扇 1 1 :覆緣 1 3 :輪轂 1 4 :輪葉 2 0 :風路 -20- (17) (17)1270635a mouth ring disposed around the suction port of the indoor fan or the outdoor fan; and a plate-shaped member that is disposed on a part or all of the outer circumference of the suction port of the indoor fan or the outdoor fan, and has a ring The height of the bulge is higher. The second object is achieved by the following integrated air conditioner, that is, for accommodating a heat exchanger in a unit; and a centrifugal fan that arranges a plurality of vanes on its hub and sets the flange A body air conditioner according to another aspect of the hub side of the vane, characterized in that: a partition plate is formed between the discharge space and the heat exchanger provided in the axial direction of the centrifugal fan; and is disposed at The partition plate forms a mouth ring of the suction port of the centrifugal fan; and the centrifugal fan is connected to the outer diameter of the wheel of the hub, which is smaller than the inner diameter of the flange inlet. The third object is achieved by the following integrated air conditioner, that is, for storing a compressor in a unit; an outdoor heat exchanger; an indoor heat exchanger; and a centrifugal indoor fan, the fan is configured with a plurality of vanes. An integrated air conditioner having a flange disposed on the other side of the hub of the vane; and an outdoor fan, wherein the indoor fan is coupled to the vane of the hub The outer diameter is larger than the inner diameter of the aforementioned margin inlet. [Embodiment] -7- (4) (4) 1270635 (Best Mode for Carrying Out the Invention) Hereinafter, an embodiment of the present invention will be described with reference to FIGS. 1 to 6 and a second diagram showing the present embodiment. Plan view of the integrated air conditioner 100. The integrated air conditioner 100 is provided inside the casing 101 to be divided into a partition 102 between the indoor side and the outdoor side. On the indoor side, a heat exchanger 103 and a centrifugal indoor fan 10 that takes in indoor air to promote heat exchange of the heat exchanger 103 are disposed, and air for discharging from the indoor fan 10 is provided to be set to be installed. The air passage 20 of the air outlet 104 on the left and right sides of the front side of the integrated air conditioner 100. The front side of the air passage 20 is formed between the heat exchanger 103 and the indoor fan 10 by the suction side casing 21, and the back side is constituted by the back side casing 19. The mouth ring 1 is disposed on the surface of the suction side casing 21 on the side of the indoor heat exchanger 101. On the side of the air passage 20 of the mouth ring 1, a centrifugal indoor fan that sucks air from the axial direction and blows it in the circumferential direction is disposed. The air discharged from the indoor fan 10 to the width direction of the integrated air conditioner is turned to 90 degrees in order to blow it from the front to the room. In the air passage 20, the air discharged from the indoor fan 10 is distributed to the left and right. As shown in the front sectional view of Fig. 4, the nose cones 2 2, 2 3 are provided. Moreover, returning to Fig. 2, the suction ring 2 having the configuration shown in Fig. 1 is attached to the outer circumference of the mouth ring 1. On the outdoor side, a compressor 1 〇 5, a heat exchanger 1600, and a centrifugal outdoor fan 30 are provided. The outdoor fan 30 is provided on the left and right sides (5) 1270635 _ surface and top surface of the casing The external air intake port 107 draws in external air to promote heat exchange of the heat exchangers 1 to 6. The indoor and outdoor fans are coupled to the fan motor 1 〇 8 , and the two fans rotate by the rotation of the fan motor 108. The compressor 105, the indoor heat exchanger 103, and the outdoor heat exchangers 1〇6 are connected by a refrigerant pipe to constitute a connected refrigeration cycle. The integrated air conditioner 1 is configured to form a dew condensation water flow path (not shown). When the air conditioner is operated, the dew condensation φ water generated in the indoor heat exchanger 1 〇3 can flow out to the bottom of the frame on the outdoor side. . The splash ring 35 shown in Fig. 1 is provided on the outer circumference of the outdoor fan 30; the dew condensation water stored at the bottom of the casing on the outdoor side is raised, and mist-like water droplets are generated and sprayed toward the outdoor heat exchanger 106. The ability of the outdoor heat exchanger 106 is improved. Next, an example in which the suction ring 2, which is an embodiment of the present invention, is applied to the indoor fan 10 will be described based on Fig. 1 . The mouth ring 1 is provided on the suction side casing 2 1 φ on the suction port side of the air passage 20 that accommodates the centrifugal indoor fan 10 . One end of the mouth ring 1 is attached to the suction side casing 21, and the other end is inserted into the suction port of the flange 11 of the indoor fan 10. The suction ring 2, which is formed into a circular arc shape, is attached to the outer circumference of the mouth ring 1. The suction ring 2 does not need to cover the entire outer circumference of the mouth ring 1, and does not necessarily have a C-shaped plate shape (a semi-arc plate-shaped rib) as in the present embodiment, or a plate-shaped member (rib without a curved portion) ) is set on the outer circumference of the mouth ring 1. In the present embodiment, an arc-shaped suction ring 2 is provided in the upper semicircular portion of the mouth ring 1. Further, the suction ring 2 may be formed as another component separate from the mouth ring 1 and installed on the suction side casing 21 of the air passage 20; or it may be integrated with the mouth ring 1 to form -9-(6) ( 6) 1270635 Shaped. The installation position of the suction ring 2 is preferably set to be larger than the outer shape (outer surface) MD2 of the ring 1 (outside the outer shape MD2). The suction ring 2 needs to be at least erected in the upper portion of the air passage 20, the convex nose cone 2 2 and the lower portion of the air passage 20 in the range of the convex nose cone 23, from the nose cone 22 to the indoor fan 1 The direction of rotation of the crucible to the extent of the nose cone 23. Further, the height SH of the suction ring 2 is preferably larger than the height MH of the mouth ring 1 from the surface of the suction side casing 2 1 . It is not necessary to have a height higher than that of the mouth ring 1, as long as the noise reduction is most effective. In the integrated air conditioner of the above configuration, the action of the indoor fan 1 说明 will be described. The suction ring 2 is not provided on the suction side of the conventional indoor fan. Therefore, noise of unknown cause may occur. So far, although the mechanism of noise generation has not been fully understood, a powerful theory has been obtained based on visual experiments of air flow. Hereinafter, it will be explained. As shown in Fig. 2, the center of the shaft of the indoor fan 1 is deviated from the center of the lateral width of the integrated air conditioner 100. This is because the relationship between the compressors 1 and 5 is accommodated, and it is desirable to shift the center of the shaft of the indoor fan away from the space in which the compressor 1 〇 5 is accommodated. In order to make the blowing air volume of the air outlets 104 provided on the left and right sides of the front surface of the main body the same, as shown in Fig. 4, the shape and height of the nose cones 22, 23 are determined. Since the heights of the nose cones on the left and right sides of the air passage 20 are different, the cross-sectional area of the air blown from the indoor fan 10 is also different from each other; when the same amount of air flows to the left and right sides of the shell, the cross section is passed. On one side of the small area, the flow rate becomes faster, and the static pressure is reduced by -10- (7) (7) 1270635. For this reason, the gas flow rate from the indoor fan 1 , will vary on the left and right sides of the case. If the airflow speed differs between the left and right sides of the air passage 20, the air passing through the air ring 1 is attracted by the air passage 20 side whose air flow speed is high and becomes a low pressure, and the air is sucked into the indoor fan 1 The flow of the airflow at the center of the suction port of the crucible is then disturbed at the fan suction port. The fluid sound due to this turbulent air flow (turbulent flow) is thought to cause the noise in front of the unit to become high. Further, the first, fourth, and fifth drawings will be described in detail. As shown in Fig. 1, the centrifugal indoor fan 10 is rotationally driven, and the indoor air is sucked into the ring 1 through the indoor heat exchanger 103. At this time, the air sucked in the outer circumferential direction of the aperture MD! of the mouth ring 1 is along the surface of the wall surface 21 of the air passage 20 and further bulges in the direction toward the fan shaft, simultaneously with the main flow from the axial direction. The surface of the mouth ring 1 is sucked into the indoor fan 1 〇. As shown in the front view of the integrated air conditioner of Fig. 4, the air discharged in the centrifugal direction by the rotation of the indoor fan 10 is distributed to the left and right sides of the air passage 20. In the air passage 20, in order to efficiently distribute the air 'discharged from the circumferential direction of the centrifugal indoor fan 10 to the left and right sides, the nose cones 22 and 23 having protrusions are provided. An example of the case where the cross-sectional area A1 on the side of the nose cone 23 of the air passage 20 is the cross-sectional area A 2 on the side of the nose cone 2 is A i < A 2 . The flow rate on the side of the nose cone 2 3 is set to v], the flow rate on the side of the nose cone 2 2 is set to v2, and the air volume q discharged from the indoor air duct 1 to the right and left air passages 20 is set to be the same. At this time, the relationship between the flow velocity v and the air volume Q and the sectional area A is v = Q / A , so v 1 > v 2 . On the left and right sides of the air passage 20, the right air flow -11 - (8) 1270635 has a different speed distribution, and the nose cone 23 side having a fast flow velocity has a lower static pressure with respect to the nose cone 22 side. Since the air easily flows to the lower pressure side, the air flowing along the wall surface of the orifice ring is introduced into the nose cone 23 side. Use Figure 5 to illustrate this situation. Fig. 5 is a perspective view of the suction port surrounded by the mouth ring 1 as seen from the indoor heat exchanger side; is a view showing the flow of air on the surface of the mouth ring 1. The paper surface is oriented, the figure on the left is a diagram in which the suction ring 2 is not provided, and the figure on the right is a diagram in which the suction ring φ 2 of the present embodiment is provided. As shown in the figure on the left, when there is no suction ring 2, the air 200 on the side of the nose cone 2 is recognized as being inhaled into the air path 20 with a low static pressure with respect to the rotation of the indoor fan 1 〇. The airflow that is formed to resist the rotation of the indoor fan 1 。. Thus, if a flow of air is generated in the fan suction port opposite to the airflow to be sucked into the center portion of the indoor fan 1, the airflow is disturbed; the result is a cause of fluid sound generation, which is considered to be a cause of an increase in noise. With respect to the flow of the air shown above, the action of the case where the suction ring 2 is provided will be described based on the right diagram of Fig. 5 . _ If the suction ring 2 is installed on the outer circumference of the mouth ring 1, the air sucked in from the room is sucked into the mouth ring 1 along the wall surface of the suction side casing 21, and it will collide with the suction ring 2, temporarily lowering the air flow speed. The state is guided to the suction port of the indoor fan 1 through the mouth ring 1. As shown in the present embodiment, the suction ring 2 is semicircularly disposed on the upper side of the mouth ring 1 (from the nose cone 2 2 of the air passage 20 whose flow velocity is increased to the arc shape of the nose cone 2 3), At the suction port of the indoor fan 10, the air velocity of the air passing through the suction ring 2 is lowered. Since the indoor fan 1 rotates counterclockwise, the indoor -12-(9) 1270635 fan 10' of the present embodiment rotates in the counterclockwise direction in FIG. 4, and the nose cone 22 and the nose cone according to the air path 20. In the positional relationship of 23, most of the air taken in by the upper side of the centrifugal indoor fan 10 covered by the suction ring 2 flows to the air passage 2 of the nose cone 23 side. Therefore, by the suction ring 2, the speed of the airflow sucked along the surface from the peripheral direction is suppressed, and the air volume ' on the side of the nose cone 23 is suppressed to become v! 4 V2, and the static pressures on the left and right sides in the casing become approximately equal. . As shown in the right diagram of Fig. 5, the air flowing along the surface of the wall surface of the orifice ring flows to the center of the indoor fan 1 , and the wind direction is unified in the same direction without turbulence. Thus, by reducing the fluid sound generated by the turbulent flow, the noise on the indoor side is lowered. The above-mentioned theory is a hypothesis. Since it is actually unclear whether or not the noise can be reduced, the noise comparison data on the indoor side in the case where the suction ring 2 is actually present is shown in Fig. 6. If compared with the same air volume, the side with the suction ring 2 has a noise 値 about i d b. According to this result, it is understood that the effect of reducing the noise on the indoor side can be obtained by using the ring 1 for the indoor fan 1 〇 φ in which the suction ring 2 is mounted on the integrated air conditioner 丨〇. The structure of the suction ring is configured such that the air passage 20 and the indoor fan 10 shown in Fig. 4 are provided in a hat-like shape at least in a counterclockwise direction from the nose cone 22 (set) In the inside of the air passage provided with the nose cone, the turbulence at the suction port of the indoor fan is suppressed, and the airflow sound is reduced, so that the noise reduction effect on the indoor side can be obtained. Further, in the present embodiment, a body type air conditioner in which two air outlets are provided on the indoor side is described, but even if it is a blow port, when the flow rate of the air-13-(10) 1270635 gas is fast, Similarly, since the surface of the air ring is sucked into the air flow of the fan from the direction around the fan, there is still a case where the airflow in the direction in which the fan rotates is prevented from flowing in, and noise is generated. Further, the number of the outlets is three or more (except for the left and right sides of the front surface, and the outlet is provided at the lower portion of the front surface), and it is also expected that a wind passage having a high flow velocity will be generated, which is also a cause of noise. In such a case, the suction ring of the present embodiment is also effective. Next, a modification of the suction ring 2 will be described using Fig. 7 . The same effect can be obtained even in the case of the mouth ring 3 shown in Fig. 7 by the effect of reducing the indoor noise generated by the suction ring. The mouth ring 3 of Fig. 7 is a shape in which the flow of the airflow is blocked, and the arc-shaped rib 4 is integrally formed and formed on the surface of the wall surface of the mouth ring. The rib 4, in the case of the indoor fan 1 旋转 rotating in the counterclockwise direction as shown in Fig. 4, is provided at least in a range from the nose cone 2 to the counterclockwise direction to the nose cone 2 3 as long as the cap is formed. can. The rib 4 of the present embodiment has a C-shaped shape that covers the fan suction port as the suction ring 2. By the rib 4, the speed of the air flowing into the fan suction port is suppressed, and the airflow speeds of the left and right sides of the air passage 20 can be adjusted; as a result, the same function as the suction ring 2 can suppress the chaos at the fan suction port. Flow, and the effect of reducing the noise level in the room can be obtained. Further, in the above-described embodiments, the suction ring 2' having an arc-shaped rib shape is formed. However, in order to reduce the flow velocity of the surface airflow 2 0 0 shown in the left diagram of Fig. 5, a straight line is provided upstream of the airflow. The plate-shaped rib can reduce noise compared to the right diagram of Fig. 5 . • 14-(11) 1270635 Next, an embodiment of the outdoor fan 30 will be described using FIG. The integrated air conditioner 第 shown in Fig. 8 is an example in which the suction ring 2 is applied to the mouth ring 5 of the outdoor fan 30. On the outdoor side, the air is taken in from the outside air inlet 〇7 by the driving of the outdoor fan 30, and is sucked into the outdoor fan 30 through the mouth ring 5 fixed to the fan cover 110, and then the air is discharged from the outdoor fan. It is blown to the outdoor heat exchanger 106 and discharged to the outside. In the present embodiment, an example of a heat exchanger to which an L shape is applied is shown. g. Thus, since the air passing through the cross-sectional area is different between the left and right sides of the discharge port of the outdoor fan 30, the airflow speeds ejected from the fan are different. As described above, "the air from the fan suction port is sucked into the low pressure side where the air flow rate is fast", so that the air flow is disturbed with respect to the air flow sucked into the center portion of the fan, and fluid sound is generated. This fluid sound leaks to the outside side and increases outdoor noise. By attaching the suction ring 2 shown in Fig. 1 to the outer circumference of the mouth ring 5, the airflow speed of the suction ring 2 is lowered, and the speed difference between the discharge airflows on both the left and right sides of the outdoor fan 30 is suppressed, and the outdoor fan is used. The static pressure distribution in the space of the indoor heat exchanger 203, the air flowing along the wall surface of the ring 5 flows to the center portion of the outdoor fan 30, and the wind direction is unified in the same direction, and the disturbance of the airflow disappears. As a result, the occurrence of the fluid sound due to the disturbance of the airflow can be removed, and the noise of the outdoor air is not added, so that the outdoor noise is lowered. Further, in the case where the outdoor fan 30 does not use the suction ring 2, the mouth ring 3 shown in Fig. 7 may be provided, and a ring having the rib 4 may be provided. The suction ring 2 shown in Fig. 1 or the mouth ring 3 shown in Fig. 7 is applicable to the -15-(12) 1270635 method, as the following three. (1) Only applicable to fans on the indoor side. (2) Fans for indoor and outdoor sides are applied separately. (3) Only applicable to fans on the outside of the room. Next, the description will be made using the figures 9 to 1 1 of the shape of the fan attached indoors and outdoors. In Fig. 9, the indoor fan 10 is composed of a hub 1 3 of a boss 12 for transmitting the rotational force of the fan motor 108 at the center of rotation, and is disposed on the hub 13 at regular intervals. The plurality of vanes 14; and the opposite side of the hub 13 are formed by a flange 11 connected to each of the vanes 14. The outer diameter D2 of the vane 14 is set to D2SLg D2 with respect to the maximum outer diameter D2S1 of the flange 11; as shown in the figure, the flow velocity distribution from the side of the flange 11 to the side of the hub 13 is appropriately adjusted. On the way, set the inflection point 1 4 a. Further, instead of providing the inflection point 1 4 a, the outer diameter may be gradually reduced from the side of the covering edge 1 1 toward the side of the hub 13 . However, the outer diameter D2H of the hub on the side of the hub 13 is D2H>DiS with respect to the inner diameter D i S of the suction flange 1 1 , and is D2H > DH with respect to the outer diameter DH of the hub. In Fig. 10, the outdoor fan 30 is provided with a hub 3 3 for transmitting a bushing 3 2 from a rotational force of the fan motor 108 at a central portion of the rotation, and is disposed at a certain interval at the hub. A plurality of vanes 3 4 on the 3 3; and a cover edge 31 connected to each of the vanes 34 on the opposite side of the hub 33. The outer diameter D2 of the vane 34 is set to D 2 s L 2 D 2 with respect to the maximum outer diameter D2S1j of the flange 31; as shown in the drawing, in order to discharge from the side of the flange 3 1 toward the side of the hub 3 3 The flow velocity distribution is optimized, and on the way, the inflection point is 3 4 a. Instead of providing the inflection point 3 4 a , the outer diameter of the outer edge 3] -16- (13) (13) 1270635 may be gradually reduced toward the side of the hub 3 3 . However, the outer diameter D2H of the hub 3 3 side, the inner diameter D! S ' of the suction port of the flange 3 1 is D 2 Η > D ! S ; relative to the outer diameter D of the hub, D 2 H = D Η. In the present embodiment, the outdoor fan 30 is mounted with a splash ring 35 for lifting the dew condensation water stored in the bottom of the outdoor side frame and sprayed toward the outdoor heat exchanger 1〇6. An example of the outer circumference of the margin 3 1 . The splash ring 35 is annularly provided on the outer circumference of the outer diameter D2SL of the flange 31. The structure of a general centrifugal fan is such that the indoor fan 1 is. In the present embodiment, although the indoor fan and the outdoor fan are both centrifugal fans, fans of different vane shapes are used. A heat exchanger is provided on the suction side with respect to the indoor fan 10, and a heat exchanger is provided on the air discharge side of the outdoor fan 30. That is, the suction space and the discharge space are separated by a fan cover (spacer) 110, and the discharge space is surrounded by the fan cover 110 and the outdoor heat exchanger 106 (although not shown, up and down direction) It is separated into the inside and outside of the unit by the top plate and the bottom plate). Further, although it is a centrifugal outdoor fan 30, the outdoor heat exchanger 1 〇 6 is also present in the axial direction of the fan. Therefore, the air that is discharged in the radial direction of the fan is forcibly flowed in the axial direction. Further, the mouth ring 5 is disposed on the partition plate, i.e., the fan cover 1 1 , and the outdoor fan 30 is disposed such that the mouth ring 5 serves as a suction port. Explain this point in detail. The outdoor fan 30 is taken from the outside air inlet 1 〇 7 The air is sucked in through the ring 5. The air sucked by the fan flows through the wall surface of the vane 34 by the rotation of the fan, and is discharged in the centrifugal direction. The air from the centrifugal outdoor fan 30 discharges -17- (14) (14) 1270635, because it is blown to the outdoor heat exchanger 100, so it is to be blown in the direction of the shaft. Blowing in the axial direction determines the wind direction by the shape of the fan cover 1 1 〇. Therefore, the air discharged from the vicinity of the covering edge 3 1 is forcibly changed to the direction of the radial direction. Here, in the case of the centrifugal fan structure shown in FIG. 9, the outer diameter D2H of the hub side is large because the outer diameter of the hub is large. Therefore, if the fan is to be used as the outdoor fan 30, the air blown by the outdoor fan 30. When flowing in the axial direction, the turbine blade surface on the hub side is distracted by the flow in the axial direction, so that the outdoor noise accompanying the fluid sound due to the turbulent flow increases, and the accompanying wheel The increase in leaf power causes an increase in the input of the fan motor 108. Therefore, the outdoor fan 30 is set to the outdoor fan 30 shown in Fig. 1 . In other words, in the outdoor fan 30, since the outer diameter D2H of the hub side and the outer diameter DH of the hub are equal, the flow of the vane is prevented from being restricted with respect to the flow in the axial direction, and the airflow in the axial direction can be reduced. The cause of the disturbance and the reduction of the work of the bucket surface on the hub side are made possible, so that it is possible to reduce the noise due to the fluid sound and reduce the motor input. The relationship between the height b2 of the discharge port of the vane 34 and the distance b3 from the rim 31 to the inflection point 34a is desirably set to 0.28 < b3/b2 < 0.58 〇 The structure of the outdoor fan is from the inside The form of the fan 10 is changed to the structure of the outdoor fan 30, and b3/b2 is set to =0.29. When the same air volume is used, the noise is reduced by about 3 dB, and the motor input is reduced by about 30%. -18- (15) 1270635 Indoor The fan 1 ο, because the air is sighed in the centrifugal direction and blows out indoors, so if the outdoor fan 30 is as small as the outdoor fan 30, the amount of air discharged will decrease. Comparing the indoor 丨 The structure of the indoor fan 10 was changed to the result of the configuration of the outdoor fan 30. In order to obtain the same air volume, the number of revolutions of the outdoor air increased by 7.3 %, and the noise increased by 2 · 5 d B. The relationship between the number of rotations η of the fan and the noise SL is SL = 601 og, and the number of rotations increases, and the indoor fan 1 噪音 whose noise also rises, and the relationship between the inner diameter D! S of the rim inlet and the wheel d2H is ideal. Dls<D2H. According to the present embodiment, it is possible to provide a one-body type air conditioner. Further, an air conditioner in which the outdoor side reduces the motor input is provided. [Effects of the Invention] According to the present invention, it is possible to reduce the noise by providing a centrifugal indoor fan via a ring for heat exchange in a room. Further, it is possible to provide an integrated air conditioner that reduces the fan motor input to an air conditioner in which an outdoor heat exchanger is disposed on the downstream side. Further, it is possible to provide a fan air conditioner that improves an indoor fan. Further, as a result of achieving the above-described effects, the fan of the surface fan 10 of the vane 14 and the fan of the fan formed in accordance with this effect is obtained by the centrifugal wind (Πΐ/η2). Therefore, the noise reduction of the noise on the indoor side of the hub side vane outer diameter and the downstream side body type air conditioner of the converter, the low noise and wind efficiency of the outdoor fan, the aforementioned description should be - 19- (16) (16) 1270635 is understandable. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a view showing the structure of a suction ring. Figure 2 is a cross-sectional view of the top surface of the integrated air conditioner. Figure 3 is a cross-sectional view of an integrated air conditioner. Figure 4 is a front sectional view of the integrated air conditioner. Fig. 5 is a view showing the wind direction around the mouth ring. Fig. 6 is a graph showing the noise reduction effect of the suction ring. Fig. 7 is a view showing the structure of the mouth ring. Figure 8 is a cross-sectional view of the top surface of the integrated air conditioner. Fig. 9 is a cross-sectional view showing the structure of an indoor side centrifugal fan. Fig. 1 is a cross-sectional view showing the structure of an outdoor side centrifugal fan. Fig. 1 is a view showing the structure of an outdoor side centrifugal fan. [Main component symbol description] 1 : Ring 2 : Suction ring 4 : Rib 1 〇: Indoor fan 1 1 : Covering edge 1 3 : Hub 1 4 : Vane 2 0 : Wind path -20- (17) (17) 1270635
3 0 :室外風扇 3 5 :飛濺環 100 : —體型空調機 1 03 :室內熱交換器 1 〇 5 :壓縮機 1 〇 6 :室外熱交換器 -213 0 :Outdoor fan 3 5 : Splash ring 100 : —Body type air conditioner 1 03 :Indoor heat exchanger 1 〇 5 :Compressor 1 〇 6 :Outdoor heat exchanger -21