200530538 (1) 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】 習知的一體型空調機的室內側，其室內熱交換器係被 配置在機組前面的中央部分，西洛可風扇（sirocco fan)或 渦輪式風扇等的離心式風扇被配置在其下游，吹出口則被 配置在室內交換器的兩側。亦即，如專利文獻1或專利文 獻2所記載，其結構爲在一體型空調機的正面，具備面對 室內交換器之空氣吸入口，自空氣吸入口吸入的空氣，經 由室內交換器’被吸進離心式風扇，再經過風路，可以從 被設置在空氣吸入口的兩側之空氣吹出口吹出。 【專利文獻1】日本實開昭53-157549號公報 【專利文獻2】日本特開平11-325505號公報 【發明內容】 (發明所欲解決之課題） 關於前述習知技術的一體型空調機，無法增加其組件 的寬度，且儘管原本是狹窄的，從室內側來看，在其正面 設置正方形的空氣吸入口，而在此空氣吸入口的左右兩邊 ，則設置縱長形的空氣吹出口。因此，爲了要確保必要的 熱交換量而吹出規定的風量，由於熱交換器的壓力損失大 ，故不得不使用高壓的風扇（西洛可風扇）。結果，會有風 -5- 200530538 (2) 扇噪音大的問題，進而會有風扇馬達的輸入高，機組消耗 電力增加，COP(性能係數=能力/電力輸入）差之類的問題 〇 這是因爲：作爲室內風扇，由於是使用其能夠輸出高 風量、高壓之輪葉係往旋轉方向傾斜大的角度且內徑大的 多翼風扇，所以風扇出口的吹出速度快，在吹出口的損失 變大’由於無法縮小被設置在組件前面的兩側之吹出口， 而必然地無法增大室內交換器的寬度的緣故。 又’此問題，由於吹出口的吹出速度慢，冷風無法到 達室內全體，故會發生室內溫度不均，到達規定溫度所需 的時間長等的問題。 亦即，若爲了提升室內交換器的熱交換性能，而增加 室內交換器的寬度，則空氣吹出口的寬度被縮小，噪音增 大；相反地，若爲了降低噪音而增加空氣吹出口的寬度， 則會有熱交換性能降低之類的問題。 本發明的目的在於提供一種一體型空調機，針對在機 組正面具有空氣吸入口、及在此空氣吸入口的左右兩邊具 有空氣吹出口之形態的一體型空調機，解決前述相反的情 況，一面降低噪音一面具有良好的熱交換性能。 (解決課題所用的手段） 前述目的，係藉由以下的一體型空調機來達成，亦即 針對具有：被收容在機組內之壓縮機、室外熱交換器、室 內熱交換器和室外風扇；被設置在前述機組的正面之空氣 -6- 200530538 (3) 吸入口；及被設置在此空氣吸入口的左右兩側之空氣吹出 口之形態的一體型空調機，其特徵爲： 將前述室內熱交換器的鰭片部分的寬度，設爲前述機 組寬度的〇_6〇〜〇·75;該室內熱交換器，係被設置成面對 前述空氣吸入口，且在其兩端具有U彎頭部，而在被夾在 兩U彎頭部之間的部分，具有鰭片。 又’前述目的’係藉由以下的一體型空調機來達成， 亦即針對具有：被收容在機組內之壓縮機、室外熱交換器 、室內熱交換器和室外風扇；被設置在前述機組的正面之 空氣吸入口；及被設置在此空氣吸入口的左右兩側之空氣 吹出口之形態的一體型空調機，其特徵爲： 將前述室內熱交換器的全體寬度，設爲前述機組寬度 的0.70〜0.85;該室內熱交換器，係被設置成面對前述空 氣吸入口，且在其兩端具有U彎頭部，而在被夾在兩U 彎頭部之間的部分，具有鰭片。 【實施方式】 (實施發明的最佳形態） 第1圖表示本發明的一實施例。機組台1載置一體型 空調機的構成要素’這些構成要素，係藉由機殼2覆蓋。 室外隔壁6，係用來區隔出吐出空間和吸入空間，並設有 作爲吸入口的室外用口環3。吐出空間，係藉由室外隔壁 6和室外熱交換器5所圍起來的空間；自室外風扇4來的 空氣，往被設置在室外用口環3的下游側之吐出空間被吐 200530538 (4) 出。在室外風扇4的上游，配置壓縮機8、吸入槽7、以 及利用其兩軸來驅動室外風扇4和室內風扇12之風扇馬 達11。風扇馬達11係藉由風扇馬達支持台10而被固定於 機組台1上。若室外風扇4旋轉，則空氣自具有壓縮機8 的房間被吸入，利用使空氣通過被設置在室外風扇4的下 游側之室外熱交換器5，將熱放出至室外。 又，在內外隔壁9的室內側，設置前面通風格柵1 9、 過濾器15、室內熱交換器21。且吸入殼20係用來將來自 此室內熱交換器21的空氣導流至室內風扇者，且兼作爲 室內殻17的一部分。自設置於吸入殼20之室內用口環13 吸入空氣係經由室內風扇12、鼻錐22、橫風向板16及縱 風向板18噴出。再者，鼻錐22係用來使自該風扇的氣流 往機組的兩側分流而加以流動者。 係被構成：若室內風扇旋轉，空氣通過前面通風格柵 1 9、過濾器1 5而被吸入，利用室內熱交換器2 1吸熱，然 後利用用來決定風扇下游的吹出氣流之複數個鼻錐22和 室內殼1 7，加以分流，再自位於室內熱交換器2 1的兩側 之吹出口 14，冷氣吹向室內側的構造。室內熱交換器21 ，在其中央部，係由具有主要是用來進行熱交換的鰭片之 部分、及使冷媒流過的配管所構成；在其兩側，係由配管 繞回的U彎頭部27所構成。將鰭片部的寬度設爲Wexf， 將鰭片部和U彎頭部全體的寬度設爲Wex。在一體型空調 機中，自室內側正面的空氣吸入口被吸入的空氣，係經由 室內熱交換器21全體的寬度Wex之中的前述鰭片部的寬 -8 - 200530538 (5) 度Wexf，而被進行熱交換，然後被吸入室內風扇12。而 且，作成使被空氣調節後的空氣，自被設置在該室內熱交 換器2 1的外邊兩側也就是機組正面的空氣吸入口的兩側 之吹出口 14，向室內吹出的構造。 再者，雖然沒有圖示出來，在室內熱交換器21的下 部，設置：承接結露水之盛水盤、及將盛水盤的水導引至 機組台1的室外側下部之導水路。 如前所述，室外熱交換器的構造，係利用鰭片和與其 密接的配管；以及在鰭片的兩端，用來使其配管多重地返 回之U彎頭部來構成。因此，利用U彎頭部被夾住其兩 端之鰭片部分，實質上爲熱交換部分，而兩端的U彎頭部 ，與鰭片部分相比’係對於熱交換幾乎沒有貢獻的部分。 大多的一體型空調機的機組寬度爲470mm至660mm(依據 冷氣能力而相異）’室內熱交換器的鰭片部的寬度，前者 爲270mm，後者爲3 7 5mm，相對於機組寬度之實質的熱交 換部分的比，大約爲0.57。 包含鰭片的兩側的U彎頭部之室內熱交換器全部寬度 ，係對前述鰭片部的寬度加上兩側的U彎頭部的長度，前 者爲330mm左右’後者爲435mm左右（相對於機組寬度的 比爲0.7〜0.66)。 這是根據：想要利用增加室內熱交換器的前面構裝面 積，來確保熱交換量之要求；以及若利用寬度方向增加熱 交換器前面面積’則機組兩側的吹出口會變狹窄，因而吹 出速度急劇地增加’使風扇的必要壓力上升變大’結果將 -9- 200530538 (6) 造成噪音增加和由於風扇輸入增加而導致消耗電力增加的 擔心，兩者一起考慮之後所決定的尺寸。 但是，對此構造而言，有以下的問題。儘管機組寬度 原本就小，室內熱交換器鰭片部的前面面積，相對於機組 寬度，由於爲如前所述的〇 . 5 7之小的値，若要吹出可確 保熱交換量的規定的風量，則熱交換器的壓力損失大，因 此不得不使用高壓的風扇（西洛可風扇）。結果，會有噪音 高的問題，進而會有風扇馬達的輸入高，機組消耗電力增 加，COP差之類的問題。 第2圖係本實施例的機組正面圖；表示相對於機組寬 度 Wu，熱交換器的寬度Wexf、Wex，以及吹出口的出口 寬度B d和機組高度方向的關係。在本實施例中，運轉操 作機機組之用的電氣零件23，係被設置在機組下部。並被 構成：機組的寬度爲Wu，高度爲Hu;熱交換器的寬度爲 Wexf、Wex，高度爲Hex;吹出口的寬度爲Bd，高度爲 Hd的矩形。 因而’熱交換器的壓力損失和吹出口的壓力損失（用 於吹出的動壓）之間的平衡，需要考量風扇的特性來加以 決定。亦即’若想要增加室內熱交換器21的寬度爲Wexf 、Wex來增加熱交換量，則會加快自吹出口 1 4吹出的風 速，其動壓急劇地增加，而需要風扇的壓力上升以上的壓 力，而會成爲空氣沒有流動的情況。 又，若想要降低吹出口的動壓，進而降低風向板的損 失，若增加吹出口 14的出口寬度Bd，則室內熱交換器22 -10- 200530538 (7) 的寬度變小，熱交換器的壓力損失增加，同時會產生無法 確保熱交換量的問題。 又’爲了要確保風量，出現要提高風扇的旋轉數的必 要，這將大幅地增加噪音，進而會導致由於風扇馬達輸入 的急劇增加而造成消耗電力的增加，故在省電力方面並不 理想。 亦即，就一體型空調機而言，在室內熱交換器的寬度 Wexf或Wex和吹出口的寬度之間，存在使風量最大並使 熱交換量最大之最適當的値。 第3圖係表示本實施例中的效果的圖；係將機組噪音 設爲習知値，相對於機組寬度（Wi〇，在改變熱交換器鰭片 部寬度（Wex)的情況，變化風量，而調查相對於機組能力 之能量消耗效率（一般稱爲COP)，這些改變將會造成如何 的變化之結果（記載値，特別是在1.5 HP以上機種的情況 ，係將能力設爲一定的情況）。利用進行實驗和模擬，導 出數値。熱交換器鰭片部寬度的習知最大値爲 Wexf/Wu = 0.57左右，並將此時的COP表示設爲COP=1.0 。風扇係使用相較於西洛可風扇，其葉輪出口的絕對速度 小（葉輪出口角，大槪/3 2 = 1 3 0以內）的離心式風扇（渦輪式 風扇）。 結果，熱交換器寬度，在比習知的最大値更大的 Wexf/Wu = 0.60以上的情況，能力往上增加，而在0.75以 上的情況，則能力急劇地降低。Wexf/Wu = 0.75以上，其 能力急劇地降低，這是由於若Wexf/Wu變大，則吹出口 -11 - 200530538 (8) 相對地變狹窄，由於吹出風速高而造成其動壓、風向板損 失增加的緣故。Wexf/WU=l的情況，理論上，完全沒有吹 出口面積，由於完全沒有風量，所以COP變成〇。 又，若Wexf/Wu小，則由於熱交換器的傳熱面積減 少、熱交換器的壓力損失急劇地增加，能力降低和風扇馬 達輸入增加的情況嚴重。在Wexf=0時，由於風量爲〇， 故COP變成0。 根據以上的結果可知，能夠確保比習知的COP= 1以 上的條件爲：相對於機組寬度（Wu)，熱交換器鰭片部寬度 (Wexf)係在 Wexf/Wu = 0.60 〜0.75 的範圍。 對空調機而言，COP提高1%以上是重要的；又，由 於僅利用風扇的性能和熱交換器的構裝狀態，便提高COP ，所以不會成爲成本上升的原因，而其結果對省電化是重 要的。這意味著：相較於現狀，作爲能夠提升COP 1 %以上 的最適當的Wexf/Wu，可以爲0.62 5至0.7;又，更理想 的値爲0.6 5至（K 7。 以上的效果，由於能夠僅利用熱交換器和風扇的傳熱 面積及噪音一定時的風扇風量便能夠得到，所以不會成爲 成本大幅上升的原因；又，也能夠謀求開發時間的縮短。 因而，就一體型空調機而言，熱交換器鰭片部的寬度 (Wexf)，相對於機組寬度，設定在0· 60〜0.75的範圍或是 前述更理想的範圍內，能夠期待：噪音方面；機組循環方 向；以及可以使吹出口的寬度（Bd)比習知小而增加吹出風 速，使冷風遍及室內全體而增加舒適性等的效果。 -12- 200530538 (9) 如前所述，若根據本實施例，針對一體型空調機，使 在被限定的機組寬度內的熱交換器的構裝寬度，根據與吹 出口的出口處之吹出動壓之間的關係，謀求最適當化，使 其構裝寬度比習知大1 〇%以上，在相同噪音時，實現高風 量化，而能增加室內熱交換量，使消耗電力少。又，作成 前述的結果，利用使吹出口的出口寬度狹窄而增加吹出速 度，使冷風可以遍及室內全體，能夠使自運轉開始的室內 溫度，變成規定的値；結果，能夠使室內全體的溫度不會 產生不均。 前述已經提示熱交換器鰭片部的寬度（Wexf)的最適値 ，但是實際的熱交換器，如第1圖所示，在鰭片部的兩側 ，存在配管的U彎頭部23，該部分雖然幾乎沒有熱交換 效果，卻是構裝上所必要的部分。吹出口的寬度（Bd)，也 是根據鰭片部的寬度（Wexf)加上兩側的U彎頭部的寬度來 決定。根據前述的數値，此U彎頭部的寬度，由於是鰭片 部的寬度（Wexf)的22%〜16%、機組寬度的13%〜9%的程 度，所以熱交換器全體寬度（WeX)的最適値，相對於前述 最適値，會較大，而成爲 Wex/Wu = 0.70〜0.85。亦即，當 將第3圖的橫軸，設爲前述熱交換器全體寬度時’能夠比 習知範圍更能提高交換熱量之寬度比，將設爲 Wex/Wu = 0.70 〜0.85 〇 因而可以得知，包含此U彎頭部之熱交換器全體寬度 的最適値，也如熱交換器鰭片部的寬度（Wexf)的最適値那 樣，存在能源消耗效率（COP)可以更高的最適當範圍。 -13- 200530538 (10) 如前所述’若將相對於機組的寬度之熱交換器的寬度 設定在最適當的範圍，則自吹出口吹出的風速也增加，室 內溫度分佈、規定溫度到達時間也能夠縮短。本實施例， 係用來使其效果更爲提高的技術。 習知的吹出口係位於機組前面，作成冷氣自機組前面 吹出的構造；相對於此，第4圖所示的吹出口的變化例， 係將吹出口 1 4擴大至機組側面側，作成伴隨著風向板i 8 的擺動，冷氣也往機組兩側面吹出的構造。若將吹出口 1 4 擴大至機組兩側面，吹出口 1 4的風速被緩和，藉由更提 升的高風量化，能力提升可以實現。通常，由於前面的裝 飾板彎曲，供給擴大用尺寸（Dd)，理想爲設成吹出口的寬 度（Bd)的20%以上。 藉此，關於室內溫度分佈，產生以下的效果。亦即， 將吹出口擴大至機組側面，並利用風向板使冷氣往兩側面 吹出，則由於吹出口比習知大，風向板的損失不會增加， 而可以使冷氣冷卻房間全體或牆壁，在穩定時，也產生輻 射冷卻的效果。 使用第1圖來說明關於室內風扇1 2的形狀。作爲室 內風扇12，其心板（覆緣）26的外徑，比側板（輪轂）2 5的 內徑小，且使輪葉（葉片）24的外徑，從側板25側到心板 26側，逐漸減少。與輪葉24的直徑在軸方向爲一定的情 況相比，能夠降低1 〇%以上的風扇馬達輸入。若採用前述 室內熱交換器的構裝狀態或吹出口的例子，第3圖所示的 能源消耗效率（COP)，進一步地提升。 -14- 200530538 (11) 再者，在前述實施例中，已 器的左右兩邊具有吹出口之一體 吹出口以外，即使有其他的吹出 若根據以上的實施例，在被 於能夠將熱交換器的構裝面積構 力固定的情況，藉由消耗電力的 升冷房效果。又，具有能夠藉由 現使用資源的最小化、成本降低 【發明之效果】 若根據本發明，能夠提供一 其機組正面設有空氣吸入口，且 側設有空氣吹出口之形態的一體 一面具有良好的熱交換性能。 【圖式簡單說明】 第1圖係表示本發明的一實 面剖面圖。 第2圖係關於第丨圖的一體 第3圖係表示室內風扇的寬 第4圖係表示一體型空調榜 圖。 【主要元件符號說明】 經說明關於在室內熱交換 型空調機，但是除了這些 口，也能夠達成效果。 限定的機組寬度之中，由 裝成最大限度，所以當能 降低、高風量化，可以提 風扇馬達輸入的降低，實 及輕量化的效果。 種一體型空調機，針對在 在此空热吸入口的左右兩 型空調機，一面降低噪音 施例的一體型空調機的平 型空調機的正面圖。 度和COP的關係的圖。 :的空氣吹出口的變化例的 200530538 (12) 1 :機組台 2 :機殼 3 :室外用口環 4 :室外風扇 5 :室外熱交換器 6 :室外隔壁 7 ··吸入槽 8 :壓縮機 9 :內外隔壁 1 〇 :風扇馬達支持台 1 1 :風扇馬達 12 :室內風扇 1 3 :室內用口環 1 4 :吹出口 1 5 :過濾器 1 6 :橫風向板 1 7 :室內殻 1 8 :縱風向板 1 9 :前面通風格柵 2 0 :吸入殻 21 :室內熱交換器 2 2 :鼻錐 23 :運轉操作部 24 :輪葉 -16- 200530538 (13) 25 :側板 2 6 _·心板 27 : U彎頭部200530538 (1) IX. Description of the invention [Technical field to which the invention belongs] The present invention relates to an integrated air conditioner. [Prior art] The indoor side of a conventional integrated air conditioner has an indoor heat exchanger placed in the center of the front of the unit, and a centrifugal fan such as a Sirocco fan or a turbo fan is placed on the On the downstream side, the air outlets are arranged on both sides of the indoor exchanger. That is, as described in Patent Document 1 or Patent Document 2, the structure is such that the front surface of the integrated air conditioner is provided with an air intake port facing the indoor exchanger, and air sucked from the air intake port is passed through the indoor exchanger. It is sucked into the centrifugal fan and then passes through the air path, and can be blown out from the air outlets provided on both sides of the air inlet. [Patent Document 1] Japanese Patent Application Publication No. 53-157549 [Patent Document 2] Japanese Patent Application Publication No. 11-325505 [Summary of Invention] (Problems to be Solved by the Invention) Regarding the integrated air conditioner of the aforementioned conventional technology, The width of its components cannot be increased, and although it is originally narrow, when viewed from the indoor side, a square air inlet is provided on the front side, and the left and right sides of this air inlet are provided with longitudinal air outlets. Therefore, in order to ensure a necessary amount of heat exchange, a predetermined amount of air is blown out, and since the pressure loss of the heat exchanger is large, a high-pressure fan (siroco fan) has to be used. As a result, there is a problem of wind -5- 200530538 (2) The fan noise is large, and then there are problems such as high fan motor input, increased power consumption of the unit, and poor COP (coefficient of performance = capacity / power input). This is Because: As an indoor fan, because it is a multi-wing fan that can output high air volume and high pressure blades that are inclined at a large angle to the rotation direction and have a large inner diameter, the blowing speed of the fan outlet is fast, and the loss at the blow outlet changes. Because of the inability to reduce the blowout ports provided on both sides of the front of the module, the width of the indoor exchanger cannot be increased. In addition, since the blowing speed of the air outlet is slow and the cold air cannot reach the entire room, problems such as uneven temperature in the room and a long time required to reach a predetermined temperature occur. That is, if the width of the indoor exchanger is increased in order to improve the heat exchange performance of the indoor exchanger, the width of the air outlet is reduced and the noise is increased. On the contrary, if the width of the air outlet is increased to reduce noise, There will be problems such as degraded heat exchange performance. An object of the present invention is to provide an integrated air conditioner, which is directed to an integrated air conditioner having an air suction port on the front of the unit and air blowout ports on the left and right sides of the air suction port. The noise side has good heat exchange performance. (Means used to solve the problem) The foregoing object is achieved by the following integrated air conditioner, that is, having a compressor, an outdoor heat exchanger, an indoor heat exchanger, and an outdoor fan housed in the unit; The air installed on the front of the aforementioned unit-6- 200530538 (3) suction port; and an integrated air conditioner in the form of air blowing ports provided on the left and right sides of the air suction port, characterized by: The width of the fin part of the exchanger is set to _6〇 ~ 〇.75 of the width of the unit; the indoor heat exchanger is set to face the air inlet and has U elbows at both ends thereof. Part, and in the part sandwiched between two U elbows, with fins. The aforementioned object is achieved by the following integrated air conditioner, that is, a compressor, an outdoor heat exchanger, an indoor heat exchanger, and an outdoor fan included in the unit; A front air inlet; and an integrated air conditioner in the form of air outlets provided on the left and right sides of the air inlet, characterized in that the entire width of the indoor heat exchanger is set to the width of the unit. 0.70 ~ 0.85; This indoor heat exchanger is set to face the air inlet and has U-bends at both ends, and fins are sandwiched between the two U-bends . [Embodiment] (Best Mode for Carrying Out the Invention) FIG. 1 shows an embodiment of the present invention. Components of the integrated air conditioner on the unit table 1 'These components are covered by the casing 2. The outdoor partition wall 6 is used to separate the discharge space and the suction space, and an outdoor mouth ring 3 is provided as a suction port. The discharge space is a space enclosed by the outdoor partition wall 6 and the outdoor heat exchanger 5; the air from the outdoor fan 4 is discharged into the discharge space provided on the downstream side of the outdoor mouth ring 3 200530538 (4) Out. On the upstream side of the outdoor fan 4, a compressor 8, a suction tank 7, and a fan motor 11 for driving the outdoor fan 4 and the indoor fan 12 using its two shafts are arranged. The fan motor 11 is fixed to the unit base 1 by a fan motor support base 10. When the outdoor fan 4 rotates, air is sucked in from the room having the compressor 8, and the air is passed through the outdoor heat exchanger 5 provided on the downstream side of the outdoor fan 4 to release heat to the outside. Further, on the indoor side of the inner and outer partition walls 9, a front ventilation grille 19, a filter 15, and an indoor heat exchanger 21 are provided. The suction casing (20) serves to guide air from the indoor heat exchanger (21) to an indoor fan and also serves as a part of the indoor casing (17). The air drawn from the indoor mouth ring 13 provided in the suction case 20 is ejected through the indoor fan 12, the nose cone 22, the cross wind direction plate 16, and the wind direction plate 18. The nose cone 22 is used to divert the airflow from the fan to both sides of the unit to flow. The system is composed: if the indoor fan rotates, the air is sucked in through the front ventilation grille 19 and the filter 15, and the heat is absorbed by the indoor heat exchanger 21, and then a plurality of nose cones are used to determine the airflow downstream of the fan. The structure 22 and the indoor casing 17 are divided, and the cold air is blown to the indoor structure from the blowing outlets 14 located on both sides of the indoor heat exchanger 21. The indoor heat exchanger 21 is composed of a portion having fins mainly used for heat exchange and pipes through which a refrigerant flows, and U-bends wound by the pipes at both sides thereof. The head 27 is constituted. The width of the fin portion is Wexf, and the width of the entire fin portion and the U-bend portion is Wex. In the integrated air conditioner, the air sucked from the air inlet on the front side of the indoor side is the width of the aforementioned fin portion of the overall heat exchanger 21 Wex-8-200530538 (5) degrees Wexf, Instead, it is heat-exchanged and sucked into the indoor fan 12. In addition, the air-conditioned air is blown into the room from the outlets 14 provided on the outer sides of the indoor heat exchanger 21, that is, on both sides of the air intake port on the front of the unit. Moreover, although not shown, a water pan that receives dew condensation water and a water guide channel that guides the water of the water pan to the lower portion of the outdoor side of the unit platform 1 are provided below the indoor heat exchanger 21. As described above, the structure of the outdoor heat exchanger is constructed by using fins and piping in close contact with them, and U-shaped elbows on both ends of the fins for returning the piping multiple times. Therefore, the U-shaped elbow is sandwiched between the fin portions at both ends, which is essentially a heat exchanging portion, and the U-elbow ends at both ends, compared with the fin portion, are portions that have little contribution to heat exchange. Most integrated air conditioners have a unit width of 470mm to 660mm (depending on the air-conditioning capacity). The width of the fin section of the indoor heat exchanger is 270mm, and the latter is 375mm. The ratio of the heat exchange part is about 0.57. The entire width of the indoor heat exchanger including the U-shaped elbows on both sides of the fin is the width of the fin part plus the length of the U-shaped elbows on both sides. The former is about 330mm and the latter is about 435mm (relatively (The ratio to the unit width is 0.7 ~ 0.66). This is based on the requirement to increase the front installation area of the indoor heat exchanger to ensure the heat exchange capacity; and to increase the front area of the heat exchanger in the width direction, the air outlets on both sides of the unit will be narrowed, so The blow-out speed increases sharply, "the necessary pressure of the fan rises." As a result, -9-200530538 (6) There is a concern that the noise will increase and the power consumption will increase due to the increase in fan input. Consider the size determined after considering both. However, this structure has the following problems. Although the width of the unit is originally small, the area of the front surface of the fin portion of the indoor heat exchanger is smaller than the width of the unit as described above, which is as small as 0.57 as described above. Air volume, the pressure loss of the heat exchanger is large, so a high-pressure fan (Siroco fan) has to be used. As a result, there are problems such as high noise, high fan motor input, increased power consumption of the unit, and poor COP. Fig. 2 is a front view of the unit of this embodiment; it shows the relationship between the widths of the heat exchangers Wexf and Wex, and the outlet width B d of the air outlet with respect to the unit width Wu and the unit height direction. In this embodiment, the electric parts 23 for operating the operator unit are provided at the lower part of the unit. And it is composed: the width of the unit is Wu, the height is Hu; the width of the heat exchanger is Wexf, Wex, and the height is Hex; the width of the blowout is Bd, and the height is Hd. Therefore, the balance between the pressure loss of the heat exchanger and the pressure loss at the blow-out port (for the dynamic pressure of the blow-out) needs to be determined by considering the characteristics of the fan. That is, 'If you want to increase the width of the indoor heat exchanger 21 to Wexf and Wex to increase the amount of heat exchange, the speed of the wind blown from the self-blowing outlet 14 will be increased, the dynamic pressure will increase sharply, and the pressure of the fan will need to rise more than The pressure will become a situation where the air does not flow. In addition, if it is desired to reduce the dynamic pressure of the air outlet and further reduce the loss of the wind direction plate, if the outlet width Bd of the air outlet 14 is increased, the width of the indoor heat exchanger 22 -10- 200530538 (7) becomes smaller, and the heat exchanger The pressure loss increases, and at the same time, there is a problem that the heat exchange amount cannot be ensured. In addition, in order to ensure the air volume, it is necessary to increase the number of rotations of the fan, which will greatly increase the noise and further increase the power consumption due to the sharp increase in the input of the fan motor, which is not ideal in terms of power saving. That is, in the case of an integrated air conditioner, between the width of the indoor heat exchanger Wexf or Wex and the width of the air outlet, there is the most suitable pump for maximizing the amount of air and the amount of heat exchange. FIG. 3 is a diagram showing the effect in the present embodiment; the unit noise is set to a conventional value, and the air volume is changed relative to the unit width (Wi0, when the width of the heat exchanger fin portion (Wex) is changed, Investigate the energy consumption efficiency (commonly referred to as COP) relative to the capacity of the unit. What are the results of these changes? (Record 値, especially in the case of models above 1.5 HP, the capacity is set to a certain situation) .Experiments and simulations are used to derive the data. The maximum known width of the heat exchanger fins is about Wexf / Wu = 0.57, and the COP expression at this time is set to COP = 1.0. Siroco fans, centrifugal fans (turbine fans) whose absolute speed at the impeller exit is small (impeller exit angle, within 槪 / 3 2 = 1 3 0). As a result, the width of the heat exchanger The maximum 値 is greater when Wexf / Wu = 0.60 or more, the capacity increases upward, and when 0.75 or more, the capacity decreases sharply. Wexf / Wu = 0.75 or more, its capacity decreases sharply, because if Wexf / Wu becomes larger, then blow out Mouth-11-200530538 (8) Relatively narrow, due to the increase in wind speed and the increase in dynamic pressure and loss of wind vane. In the case of Wexf / WU = 1, theoretically, there is no area for the outlet, because there is no The amount of air flow, so COP becomes 0. Moreover, if Wexf / Wu is small, the heat transfer area of the heat exchanger decreases, the pressure loss of the heat exchanger increases sharply, and the situation of reduced capacity and increased fan motor input is serious. In Wexf = At 0, since the air volume is 0, the COP becomes 0. From the above results, it can be seen that the condition that can ensure that the conventional COP = 1 or more is: the width of the heat exchanger fin portion (Wexf relative to the unit width (Wu)) ) Is in the range of Wexf / Wu = 0.60 to 0.75. For air conditioners, it is important to increase the COP by more than 1%; and because the performance of the fan and the structure of the heat exchanger are used to increase the COP, It will not be the cause of rising costs, and the result is important for power saving. This means that compared to the status quo, as the most appropriate Wexf / Wu that can increase COP by more than 1%, it can be 0.62 5 to 0.7; and , More ideally Is 0.6 5 to (K 7. The above effects can be obtained by using only the heat transfer area of the heat exchanger and the fan, and the fan air volume when the noise is constant, so it will not cause a significant increase in cost; also, The development time can be shortened. Therefore, in the case of an integrated air conditioner, the width (Wexf) of the fin portion of the heat exchanger is set to a range of 0. 60 to 0.75 or a more desirable range with respect to the unit width. In the interior, the following aspects can be expected: noise, the unit circulation direction, and the effect that the width (Bd) of the air outlet can be made smaller than the conventional one to increase the blowing wind speed, and the cold air can be spread throughout the room to increase comfort. -12- 200530538 (9) As mentioned above, according to this embodiment, for the integrated air conditioner, the structure width of the heat exchanger within the limited unit width is based on the The relationship between the output pressure is optimized to make the width of the structure more than 10% larger than the conventional one. At the same noise, high wind quantification is achieved, and the amount of indoor heat exchange can be increased to reduce power consumption. In addition, by making the foregoing result narrow the width of the outlet of the outlet and increasing the blowing speed so that cold air can be spread throughout the room, the room temperature since the start of the operation can be reduced to a predetermined level; as a result, the temperature of the entire room can be reduced. Unevenness will occur. The foregoing has suggested that the width (Wexf) of the fin portion of the heat exchanger is optimal, but the actual heat exchanger, as shown in FIG. 1, has U-shaped elbows 23 on both sides of the fin portion. Although the part has almost no heat exchange effect, it is a necessary part in the construction. The width (Bd) of the air outlet is also determined based on the width of the fin section (Wexf) plus the width of the U-bends on both sides. According to the foregoing figures, the width of the U-bend is approximately 22% to 16% of the width of the fin section (Wexf) and 13% to 9% of the width of the unit. ), The optimum value is larger than the aforementioned optimum value, and becomes Wex / Wu = 0.70 ~ 0.85. In other words, when the horizontal axis of FIG. 3 is set to the entire width of the heat exchanger, the width ratio of heat exchange can be increased more than the conventional range. Wex / Wu = 0.70 to 0.85 〇 can be obtained It is known that the optimum width of the entire width of the heat exchanger including the U-bend is also the most suitable range in which the energy consumption efficiency (COP) can be higher as the width of the heat exchanger fin portion (Wexf) is optimal. . -13- 200530538 (10) As mentioned above, "If the width of the heat exchanger relative to the width of the unit is set to the most appropriate range, the wind speed from the blower outlet will also increase, and the indoor temperature distribution and the predetermined temperature arrival time will be increased. It can also be shortened. This embodiment is a technique for further improving the effect. The conventional blow-out port is located in front of the unit and has a structure in which cold air is blown out from the front of the unit. In contrast, the modified example of the blow-out port shown in Figure 4 is to expand the blow-out port 14 to the side of the unit, and is accompanied by The structure of the wind vane i 8 swings, and the cold air is also blown to both sides of the unit. If the air outlet 14 is enlarged to both sides of the unit, the wind speed of the air outlet 14 is moderated, and the capacity can be improved by the higher wind quantization. Generally, the front decorative plate is bent, and the size (Dd) for supply expansion is preferably set to 20% or more of the width (Bd) of the blow-out port. Thereby, the following effects are produced about the indoor temperature distribution. That is, if the air outlet is enlarged to the side of the unit, and the cold air is blown out to both sides by using the wind direction plate, the air outlet will be larger than the conventional one, and the loss of the wind direction plate will not increase, so that the cold air can cool the entire room or the wall. When stable, the effect of radiative cooling is also produced. The shape of the indoor fan 12 will be described using FIG. 1. As the indoor fan 12, the outer diameter of the core plate (covering edge) 26 is smaller than the inner diameter of the side plate (hub) 25, and the outer diameter of the vane (blade) 24 is from the side plate 25 side to the core plate 26 side ,gradually decreases. Compared with the case where the diameter of the vane 24 is constant in the axial direction, the fan motor input can be reduced by more than 10%. If the structure of the indoor heat exchanger or the example of the air outlet is used, the energy consumption efficiency (COP) shown in Fig. 3 is further improved. -14- 200530538 (11) Furthermore, in the foregoing embodiment, the left and right sides of the device have a body outlet other than the outlet. Even if there are other outlets, according to the above embodiment, the heat exchanger can be In the case where the structural area is fixed, the effect of increasing the cooling room by the power consumption. In addition, the present invention can minimize the current resources and reduce the cost. [Effect of the invention] According to the present invention, it is possible to provide an integrated surface in which a unit is provided with an air inlet on the front side and an air outlet on the side. Good heat exchange performance. [Brief Description of the Drawings] Fig. 1 is a real sectional view of the present invention. Fig. 2 shows the integration of Fig. 丨 Fig. 3 shows the width of the indoor fan. Fig. 4 shows the list of integrated air conditioners. [Description of Symbols of Main Components] The indoor heat exchange type air conditioner has been described, but in addition to these ports, the effect can be achieved. Among the limited unit widths, it is installed to the maximum, so when it can be reduced and the high wind is quantified, the input of the fan motor can be reduced, and the effect of weight reduction can be achieved. An integrated type air conditioner is a front view of a flat type air conditioner of the integrated type air conditioner of this embodiment in which the left and right type air conditioners at the air heat inlet are reduced in noise. The relationship between degree and COP. : 200530538 (12) Example of the change of the air blowing outlet 1: Unit table 2: Cabinet 3: Outdoor mouth ring 4: Outdoor fan 5: Outdoor heat exchanger 6: Outdoor partition 7 ·· Suction tank 8: Compressor 9: Inside and outside partitions 1 〇: Fan motor support stand 1 1: Fan motor 12: Indoor fan 1 3: Indoor mouth ring 1 4: Blowout port 1 5: Filter 1 6: Cross wind direction board 1 7: Indoor shell 1 8 : Wind direction board 1 9: Front ventilation grille 2 0: Suction shell 21: Indoor heat exchanger 2 2: Nose cone 23: Operation control unit 24: Blade-16- 200530538 (13) 25: Side plate 2 6 _ · Heart plate 27: U curved head
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