1276760 (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- (2) 1276760 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- (3) 1276760 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0.60〜0.75;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，係藉由機殻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 -7 - (4) 1276760 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和室內風扇丨2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jg 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 室內殼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 (5) 1276760 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 75mm，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3 3 0mm左右，後者爲43 5 mm左右（相對於機組寬度的 比爲0.7〜0 · 6 6)。 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- (6) 1276760 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0 · 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 力口，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Bd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 (7) 1276760 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（Wu)，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 ·5ΗΡ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，大槪冷2=130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 - (8) 1276760 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=1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0。 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=〇時，由於風量爲〇， 故COP變成〇。 根據以上的結果可知，能夠確保比習知的COP = l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0.625至0.7;又，更理想 的値爲〇 . 6 5至0 · 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，熱交換器鳍片部的寬度 (Wexf)，相對於機組寬度，設定在〇.60〜0.75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- 12767601276760 (1) Description of the Invention [Technical Field of the Invention] The present invention relates to an integrated air conditioner. [Prior Art] In the indoor side of a conventional integrated air conditioner, the indoor heat exchanger is disposed at the center of the front of the unit, and a centrifugal fan such as a Sirocco fan or a turbo fan is disposed. Downstream, the blowout outlets are placed on either side of the indoor exchanger. In other words, as described in Patent Document 1 or Patent Document 2, the air intake port facing the indoor exchanger is provided on the front surface of the integrated air conditioner, and the air taken in from the air intake port is passed through the indoor exchanger. The centrifugal fan is sucked in, and then passes through the air path, and can be blown out from the air blowing ports provided on both sides of the air suction port. [Patent Document 1] Japanese Laid-Open Patent Publication No. Hei No. Hei. No. Hei. No. Hei. No. Hei. No. Hei. No. Hei. No. 11-325505. It is impossible to increase the width of the components, and although it is originally narrow, a square air suction port is provided on the front side from the indoor side, and a vertically long air blowing port is provided on the left and right sides of the air suction port. Therefore, in order to ensure a required amount of heat exchange and to blow a predetermined amount of air, since the pressure loss of the heat exchanger is large, a high-pressure fan (Syroco fan) has to be used. As a result, there will be a problem that the wind-5-(2) 1276760 fan is loud, and there will be a problem that the fan motor input is high, the unit consumes power, and the COP (performance coefficient = capability/power input) is poor. Because the indoor fan is a multi-blade fan that can output a high air volume and a high-pressure wheel blade that is inclined at a large angle in the rotation direction and has a large inner diameter, the fan outlet is blown at a high speed, and the loss at the air outlet is changed. Large, since it is impossible to reduce the air outlets provided on both sides of the front side of the assembly, it is inevitable that the width of the indoor exchanger cannot be increased. Further, this problem is caused by the fact that the blowing speed of the air outlet is slow and the cold air cannot reach the entire interior of the room, so that the indoor temperature is uneven and the time required to reach the predetermined temperature is long. That is, if the width of the indoor exchanger is increased in order to increase the heat exchange performance of the indoor exchanger, the width of the air outlet is reduced, and the noise is increased. Conversely, if the width of the air outlet is increased in order to reduce noise, There will be problems such as reduced heat exchange performance. An object of the present invention is to provide an integrated air conditioner having an air intake port on the front side of the unit and an air blower having air blowing ports on the left and right sides of the air intake port, and the opposite situation is solved. The noise side has good heat exchange performance. (Means for Solving the Problem) The above object is achieved by the following integrated air conditioner, that is, for a compressor, an outdoor heat exchanger, an indoor heat exchanger, and an outdoor fan that are housed in a unit; An integrated air conditioner in the form of an air -6-(3) 1276760 suction port provided on the front side of the unit; and an air blowing port provided on the left and right sides of the air suction port, characterized in that: the indoor heat is The width of the fin portion of the exchanger is set to 0.60 to 0.75 of the aforementioned unit width; the indoor heat exchanger 'is disposed to face the aforementioned air suction port and has a U-bend head at both ends thereof The portion sandwiched between the two U-bends has fins. Moreover, the above 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 that are housed in the unit; An air intake port on the front side; and an integrated air conditioner in the form of an air outlet port provided on the left and right sides of the air intake port, wherein the entire width of the indoor heat exchanger is set to the unit width 0.70 to 0.85; the indoor heat exchanger is disposed to face the aforementioned air suction port, and has a U-bend portion at both ends thereof, and has a fin at a portion sandwiched between the two U-bend portions sheet. [Embodiment] (Best Mode for Carrying Out the Invention) Fig. 1 shows an embodiment of the present invention. The components of the integrated air conditioner are placed on the unit table 1, and these components are covered by the casing 2. The outdoor partition wall 6 is for partitioning the discharge space and the suction space, and is provided with an outdoor ring 3 as a suction port. The discharge space is a space surrounded by the outdoor partition wall 6 and the outdoor heat exchanger 5; the air from the outdoor fan 4 is discharged to the discharge space provided on the downstream side of the outdoor ring 3 - ( 4) 1276760. Upstream 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 丨2 by the two axes thereof are disposed. The fan motor 11 is fixed to the unit block 1 by the fan motor support table 10. When the outdoor fan 4 rotates, air is taken 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 air jg 4 to discharge the heat to the outside. Further, a front ventilation grille 19, a filter 15, and an indoor heat exchanger 21 are provided on the indoor side of the inner and outer partition walls 9. Further, the suction casing 20 is for guiding the air from the indoor heat exchanger 21 to the indoor fan, and also serves as a part of the indoor casing 17. The air intake from the indoor air supply port 13 provided in the suction casing 20 is discharged through the indoor fan 12, the nose cone 22, the cross wind direction plate 16, and the vertical wind direction plate 18. Further, the nose cone 22 is used to flow the airflow from the fan to both sides of the unit for flow. The system is configured such that if the indoor fan rotates, the air is sucked through the front ventilation grille 19 and the filter 15, and the indoor heat exchanger 21 absorbs heat, and then uses a plurality of nose cones for determining the blown airflow downstream of the fan. 22 and the inner casing 17 are shunted, and the air outlets 14 are located on both sides of the indoor heat exchanger 21, and the cold air is blown toward the indoor side. The indoor heat exchanger 21 is composed of a portion having fins mainly for heat exchange and a pipe through which a refrigerant flows, and a U-turn which is wound around the pipe on both sides thereof. The head 27 is constructed. 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 taken in from the air intake port on the front side of the indoor side is made through the width (5) 1276760 degrees Wexf of the fin portion among the widths Wex of the entire indoor heat exchanger 21 The heat is exchanged and then sucked into the indoor fan 12. Further, the air-conditioned air is formed so as to be blown out from the air outlets 14 provided on both sides of the indoor heat exchanger 21, that is, on both sides of the air intake port on the front side of the unit. Further, although not shown, a water tray for receiving dew condensation water and a water conduit for guiding the water of the water tray to the lower portion of the outdoor side of the unit block 1 are provided in the lower portion of the indoor heat exchanger 21. As described above, the structure of the outdoor heat exchanger is constituted by the fins and the pipes which are in close contact therewith, and the U-bend heads for returning the pipes to the ends of the fins at multiple ends. Therefore, the U-bend portion is sandwiched between the fin portions at both ends thereof, which is substantially a heat exchange portion, and the U-bend portions at both ends are portions which are hardly contributing to heat exchange as compared with the fin portions. Most integrated air conditioners have a unit width of 470mm to 660mm (different depending on the air-conditioning capacity). The width of the fins of the indoor heat exchanger is 270mm for the former and 3 75mm for the latter, which is the relative heat of the unit width. The ratio of the exchanged parts is approximately 0.57. The entire width of the indoor heat exchanger including the U-bend heads on both sides of the fin is the length of the fin portion plus the length of the U-bend head on both sides, the former being about 330 mm, and the latter being 43 5 The mm is about (the ratio with respect to the unit width is 0.7~0 · 6 6). This is based on the fact that the front mounting area of the indoor heat exchanger is required to ensure the heat exchange amount; and if the front area of the heat exchanger is increased by the width direction, the air outlets on both sides of the unit are narrowed. The blowing speed is drastically increased, and the necessary pressure rise of the fan is increased. As a result, the noise is increased by -9-(6) 1276760 and the power consumption is increased due to an increase in the fan input, and the two are determined together. However, this configuration has the following problems. Although the unit width is originally small, the front area of the fin portion of the indoor heat exchanger is relative to the unit width, and since it is a small crucible of 0 · 5 7 as described above, it is required to blow out the regulations for ensuring the amount of heat exchange. The air volume, the pressure loss of the heat exchanger is large, so a high-pressure fan (Syroco fan) has to be used. As a result, there is a problem of high noise, and there is a problem that the input of the fan motor is high, the power consumption of the unit is increased, and the COP is poor. Fig. 2 is a front view of the unit of the present embodiment; showing the relationship between the widths Wexf, Wex of the heat exchanger, and the outlet width Bd of the blow port with respect to the unit width Wu, and the height direction of the unit. In the present embodiment, the electrical component 23 for operating the operating unit is disposed in the lower portion of the unit. It is composed of: the width of the unit is Wu and the height is Hu; the width of the heat exchanger is Wexf, Wex, and the height is Hex; the width of the outlet is Bd, and the height is Hd. Therefore, the balance between the pressure loss of the heat exchanger and the pressure loss of the blow port (for the dynamic pressure to be blown) needs to be determined in consideration of the characteristics of the fan. In other words, if the width of the indoor heat exchanger 21 is increased to Wexf or Wex to increase the heat exchange amount, the wind speed blown from the air outlet 14 is increased, and the dynamic pressure is sharply increased, and the pressure of the fan is required to rise or higher. The pressure will become a condition in which the air does not flow. Further, 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 (7) 1276760 becomes small, and the pressure loss of the heat exchanger is reduced. The increase will also cause problems that cannot ensure the amount of heat exchange. Further, in order to secure the air volume, it is necessary to increase the number of rotations of the fan. This greatly increases the noise, which in turn causes an increase in power consumption due to a sharp increase in the input of the fan motor, which is not preferable in terms of power saving. That is, in the integrated air conditioner, between the width Wexf or Wex of the indoor heat exchanger and the width of the air outlet, there is an optimum amount of air which maximizes the amount of air and maximizes the amount of heat exchange. Fig. 3 is a view showing the effect in the present embodiment; the unit noise is set as a conventional one, and the air volume is changed while changing the width (Wex) of the fin portion of the heat exchanger with respect to the unit width (Wu). And the investigation of the energy consumption efficiency (generally called COP) relative to the capacity of the unit, the result of these changes will be caused by the changes (recorded, especially in the case of models above 1 · 5 ,, the ability to set a certain situation ). Using experiments and simulations, the number is derived. The conventional maximum 値 of the fin portion width of the heat exchanger is Wexf/Wu = 0.57, and the COP at this time is expressed as COP = 1.0. The fan uses a centrifugal fan (turbine fan) whose absolute speed is smaller than the sirocco fan (the impeller exit angle is 2=130 or less). As a result, the heat exchanger width is increased in the case where Wexf/Wu = 0.60 or more larger than the conventional maximum enthalpy, and the capacity is sharply decreased in the case of 0.75 or more. When Wexf/Wu = 0.75 or more, the capacity is drastically lowered. This is because if Wexf/Wu becomes large, the blower outlet -11 - (8) 1276760 becomes relatively narrow, and the dynamic pressure and the wind direction plate are caused by the high blown wind speed. The reason for the increase in losses. In the case of Wexf/Wu = 1, theoretically, there is no blowing area at all, and since there is no air volume at all, the COP becomes zero. Further, when Wexf/Wu is small, the heat transfer area of the heat exchanger is reduced, and the pressure loss of the heat exchanger is rapidly increased, and the capacity is lowered and the fan motor input is increased. At Wexf=〇, since the air volume is 〇, the COP becomes 〇. From the above results, it can be confirmed that the above-described condition of COP = l can be ensured that the heat exchanger fin width (Wexf) is in the range of Wexf/Wu = 0.60 to 0.75 with respect to the unit width (Wu). For air conditioners, it is important to increase the COP by more than 1%. Moreover, since only the performance of the fan and the state of the heat exchanger are used, the COP is increased, so that it does not become a cause of cost increase, and the result is Electrochemistry is important. This means that compared to the current situation, the most appropriate Wexf/Wu, which can increase the COP by more than 1%, can be 0.625 to 0.7; and, more ideally, it is 〇 6 5 to 0 · 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 at a certain noise level, so that the cost is not greatly increased, and the development time can be shortened. Therefore, in the integrated air conditioner, the width (Wexf) of the fin portion of the heat exchanger is set in the range of 〇60 to 0.75 or more preferably in the above range with respect to the unit width, and it is expected that noise is The cycle direction of the unit; and the effect that the width (Bd) of the air outlet can be made smaller than that of the conventional one, and the wind speed can be increased, and the cold air can be spread throughout the room to increase the comfort. -12- 1276760
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- (10) 1276760 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1 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 14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（D d )，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12的形狀。作爲室 內風扇12，其心板（覆緣）26的外徑，比側板（輪轂）25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。 (11) 1276760 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1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機 圖0 【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 在此空氣吸入口的左右兩 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C Ο P的關係的圖。 :的空氣吹出口的變化例的 -15- (12) (12)1276760 1 :機組台 2 :機殻 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 13 :室內用口環 14 :吹出口 1 5 :過濾器 1 6 :橫風向板 17 :室內殼 1 8 :縱風向板 1 9 :前面通風格柵 20 :吸入殼 21 :室內熱交換器 22 :鼻錐 23 :運轉操作部 2 4 :輪葉 -16- (13)1276760 2 5 :側板 2 6 ··心板 27 : U彎頭部As described above, according to the present embodiment, with respect to the integrated air conditioner, the configuration width of the heat exchanger within the defined unit width is based on the relationship with the blowout dynamic pressure at the outlet of the air outlet. In order to optimize the size, the width of the package is made larger than the conventional one by more than 1%, and when the same noise is used, the high air volume can be quantified, and the amount of indoor heat exchange can be increased to reduce the power consumption. In addition, as a result of the above, the outlet width of the outlet is narrowed, and the blowing speed is increased, so that the cold air can be spread over the entire interior of the room, and the indoor temperature from the start of the operation can be changed to a predetermined temperature. As a result, the temperature of the entire room can be prevented. Will produce unevenness. The above has suggested the optimum width of the heat exchanger fin portion (Wexf), but the actual heat exchanger, as shown in Fig. 1, has U-bend head 23 of the pipe on both sides of the fin portion, which Although there is almost no heat exchange effect, it is a necessary part of the structure. The width (Bd) of the blower outlet is also determined by the width of the fin portion (Wexf) plus the width of the U-bend head on both sides. According to the above number, the width of the U-bend head is 22% to 16% of the width (Wexf) of the fin portion, and 13% to 9% of the width of the unit, so the entire width of the heat exchanger (Wex The most appropriate, relative to the above-mentioned optimum, will be larger, and become 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 the exchange heat can be increased more than the conventional range, and it is possible to set Wex/Wu = 0.70 to 0.85. It is known that the optimum width of the entire heat exchanger including the U-bend head is also the most suitable for the energy consumption efficiency (COP), as is the optimum width of the heat exchanger fin portion (Wexf). range. -13- (10) 1276760 As described above, if the width of the heat exchanger with respect to the width of the unit is set to the most appropriate range, the wind speed blown from the outlet is also increased, and the indoor temperature distribution and the specified temperature arrival time are increased. Can also be shortened. This embodiment is a technique for improving the effect. The conventional air outlet is located in front of the unit to create a structure in which cold air is blown from the front of the unit. On the other hand, in the variation of the air outlet shown in Fig. 4, the air outlet 14 is extended to the side of the unit, which is accompanied by The wind direction plate 18 is oscillated, and the cold air is also blown to the sides of the unit. If the blower port 14 is enlarged to both sides of the unit, the wind speed of the blower port 14 is alleviated, and the capacity increase can be achieved by quantifying the higher wind. Usually, since the front decorative plate is bent, the supply expansion size (D d ) is desirably set to 20% or more of the width (Bd) of the air outlet. Thereby, regarding the indoor temperature distribution, the following effects are produced. That is, the blower outlet is extended to the side of the unit, and the wind direction plate is used to blow the cold air to both sides. Since the blower outlet is larger than conventionally, the loss of the wind direction plate does not increase, and the cold air can cool the entire room or the wall. When it is stable, it also produces the effect of radiant cooling. The shape of the indoor fan 12 will be described using FIG. 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. The fan motor input can be reduced by more than 1% compared to the case where the diameter of the vane 24 is constant in the axial direction. The energy consumption efficiency (COP) shown in Fig. 3 is further improved by the example of the configuration of the indoor heat exchanger or the outlet. (11) 1276760 Further, in the above-described embodiment, the left and right sides of the device have a blow-out port other than the body outlet, and if there is another blow, according to the above embodiment, the heat exchanger can be assembled. The case where the area structure force is fixed, by consuming the power of the cold room effect. Further, it is possible to minimize the cost and reduce the cost by using the present invention. [Effect of the Invention] According to the present invention, it is possible to provide an integral side in which the air suction port is provided on the front side of the unit and the air blowing port is provided on the side. Good heat exchange performance. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a cross-sectional view showing a solid surface of the present invention. Fig. 2 is an integrated view of Fig. 1 showing the width of the indoor fan. Fig. 4 shows an integrated air conditioner. Fig. 0 [Description of main components] The description relates to an indoor heat exchange type air conditioner, but these are described. The mouth can also achieve results. Among the limited unit widths, it is installed to the maximum. Therefore, when it can be reduced and the wind is quantized, the fan motor input can be reduced, and the weight reduction effect can be achieved. An integrated air conditioner is a front view of a flat air conditioner of an integrated air conditioner that reduces noise in the left and right air conditioners of the air intake. A graph of the relationship between degrees and C Ο P. : -15- (12) (12) 1276760 of the air outlet change: Unit 2: Case 3: Outdoor ring 4: Outdoor fan 5: Outdoor heat exchanger 6: Outdoor partition 7: Inhalation Slot 8: Compressor 9: Inner and outer partitions 1 〇: Fan motor support table 1 1 : Fan motor 12 : Indoor fan 13 : Indoor ring 14 : Outlet 1 5 : Filter 1 6 : Cross wind direction plate 17 : Indoor case 1 8 : longitudinal wind direction plate 1 9 : front ventilation grille 20 : suction casing 21 : indoor heat exchanger 22 : nose cone 23 : operation operation portion 2 4 : vane - 16 - (13) 1276760 2 5 : side plate 2 6 ··心板27 : U curved head
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