1320094 •九、發明說明： 【明所屬之技術領域】 古、，^發明係有關於一種用於冷卻系統之熱交換裳置，更 .式熱交換裝置。較為冷媒由上而下流動之喷淋 【先前技術】 冷卻的應用早已衧之& i = + , 調裝置中，係包含四個Γ要杜 習用之冷康空 •發哭及冷凝尹。户- 兀件·壓縮機、膨脹裝置、蒸 :口。〇在崧發器的熱交換上，大多係藉著 *表面，以熱傳導之上標流體的管 w 3目私流體之熱量由較炉 冷卻的目的。目前由於節約資源的二 ν且々凍二凋乐統所使用的冷媒亦因能 格也隨之飄高，因此，如= 牛乂換Μ的减下，減低在冷;東空調I统中的冷媒 ，、里’以降低設備成本並兼顧環境保護 的重要課題。 取馮〇人 近年♦來’在冷床空調系統中的蒸發器上獲得許多改 依據蒸發器的設計可大致分為直膨式、滿溢式與喷淋 乂直膨式热發器係屬於外殼内管式熱交換器之一種，其 在管内側流動的是冷禅而古&彳 疋々跺，而在叙側流動的是目標流體。铁1320094 • Nine, invention description: [Technical field to which it belongs] The ancient, and the inventions are related to a heat exchange device for a cooling system, and a heat exchange device. Spraying the flow of the refrigerant from top to bottom [Prior Art] The application of cooling has long been used in & i = +, and the adjustment device contains four cold and cold airs that are used in practice. • Cry and condense Yin. Household - equipment, compressor, expansion device, steaming: mouth. In the heat exchange of the hair dryer, most of the heat of the private fluid through the surface of the heat transfer tube is cooled by the furnace. At present, the refrigerant used by the resource-saving two-dimensional and frozen-frozen system has also risen because of the energy level. Therefore, if the reduction of the burdock is reduced, the reduction is in the cold; Refrigerant, and Li's important issues to reduce equipment costs and take into account environmental protection. Take Feng Weiren in recent years ♦ Come to 'on the evaporator in the cold bed air conditioning system to get a lot of changes based on the design of the evaporator can be roughly divided into direct expansion, overflow and spray 乂 direct expansion type of hair dryer belongs to the shell One type of inner tube heat exchanger, which flows through the inside of the tube is a cold zen and an ancient amp; while on the side of the tube is a target fluid. iron
=，為了防止管内液態冷媒在蒸發不完全之狀態下被吸I 壓縮機中而造成壓縮機受損，因此在使用直膨式蒸發器之 冷4空調系統中，必須提高壓縮機入口端的過熱度，因而 19847 1320094 * · 造成壓縮機的耗功。 此外’滿溢式蒸發器亦屬於外殼内管式熱交換器之一 種’但其在管内側流動的是目標流體，在殼側流動的是冷 媒。由於滿溢式蒸發器係在蒸發器殼體上方設置用以回^ -被蒸發之冷媒，因此液態冷媒較不易進入壓縮機入口端。 •二=由於滿式洛發器係將管子浸泡於蒸發器殼體中的 液態冷媒中，因此需要較多量的液態冷媒，造成所需要的 冷媒充填量比直膨式蒸發器多了 一倍以上之量，致增加設 鲁備成本與環境負擔。 3 a 第1圖係顯示習知之喷淋式蒸發器1〇1之剖視圖。如 •第1圖所示，噴淋式蒸發器101係具有殼體1015、配置 於殼體1015内侧上部的噴淋器1011、以及以水平方向配 置於贺淋器1 〇 Π下方的複數支熱傳管丨〇丨3。液態冷媒自 D貧淋器1011上方的入口進入後，經由形成於噴淋器m 下表面之複數個小孔（未顯示）而向下滴灑於設於下方之 鲁熱傳管1013。藉由將液態冷媒濃入交錯排列的熱傳管 1013陣列中’而在各個熱傳管1013表面形成冷媒覆膜， ，從而對熱傳管1013進行熱交換作用。如第1圖中之虛線 • 所示’蒸發後之冷媒會經由殼體101 5與噴淋器1 〇 11之間 的間隙往上方被排出。 此外，如中華民國專利第M247805號所揭露，係利用 一溢流盤及一淋灑盤將液態冷媒向下滴灑於熱傳管上，藉 此達到熱交換之功效。除此之外，尚有美國專利 5836382、6167713、6868695號利用改變噴淋器的結構來 6 19847 1320094 達到m !_使液怨冷媒能擴大滴淋在熱傳管上的效果。再 者，亦有美國專利5904807號利用改變蒸發器上部構造， 直接將液態冷媒注入新式噴灑結構中達到擴大噴灑之效 果。 ▲然而，上述之噴淋式蒸發器往往為使噴淋裴置能讓液 態冷媒大範圍地滴淋在下方的熱傳管上，遂將噴淋裝置設 置在離蒸發器上方之冷媒入口較遠的位置，以獲得較大之 喷灑面積，但也因此使得蒸發器内能夠配置熱傳管之空間 釀咸〆故為了達到期望之熱交換效率，必須相對地增加蒸 發器殼體之尺寸。因此，習知之脅淋式蒸發器不但造成^ 間的浪費，相對亦使得材料成本增加而增加了製造之成 本0 Q此如何有效解決前揭技術所存在之 液態冷媒由上而下流動方式的蒸發器，開發出一種可= ==時不需增加尺寸之喷淋式熱交換裝置: ^ \^成本降低，或於相同殼體尺寸下可設置較多數 里之元、·官之喷淋式熱交換裝置，以 升熱交換效率及避旁介門、_蕃a …乂換面積、提 解決之課題 ，浪費’正是目前冷卻系統所函待 【發明内容】 在上所述先前技術之缺點，本發明之主要目的即 種能夠增進空間利㈣之喷淋式熱交換震/ 置，另一目的在於提供一種喷淋式熱交換裝 在使用相同數量之熱傳管的同時減小其本體尺 19847 7 1320094 位於實施例：，該喷淋單元係設置在使其喷琳面 置，而於二、。”側算起約殼體内徑之5至25%的位 所設置二群組之熱傳管之間 取I:: 為殼體内徑之侧的位置。藉此，可求 取‘、、、傳^之最大配置率。 於另一較佳實施例中，該噴淋單元係設置在使宜 =,由，部下側算起約殼體内徑之5至抓的位 J:二—群組之熱傳管與該第二群組之熱傳管之間所 。又置之，一個滴淋盤係設置在使其盤面位於由殼體頂 部下側算起約為殼體内徑之2〇至3〇%的位置，於該二 群組之熱傳管與該第三群組之熱傳管之間収置之至小 一個滴淋盤係設置在使其盤面位於由殼體頂部下側算^ ，為，體内徑之45至50%的位置。藉此，亦可求取熱傳 ^之敢大配置率。 鲁 於一較佳實施例中，上述熱傳管之相鄰上下列之各熱 傳管係呈交錯配置，以便使流經較上列之熱傳管而滴荩^ 冷媒可通過次一列之熱傳管之間而滴落至再次一列之熱 傳管上。藉此’能夠爭取最大的空間利用率，更有效去地 在熱交換裝置内配置熱傳管。 卞 【實施方式】 以下參照附圖說明本發明之實施例。該等圖式俱為簡 化之示意圖式’且僅例示與本發明有關之元件，且，;一 件之實際形狀或尺寸比例並非本發明之特徵，而可 19847 10 !32〇〇94=, in order to prevent the liquid refrigerant in the pipe from being sucked into the compressor in the state of incomplete evaporation, the compressor is damaged. Therefore, in the cold 4 air conditioning system using the direct expansion evaporator, the superheat of the inlet end of the compressor must be increased. Thus, 19847 1320094 * · caused the power consumption of the compressor. In addition, the 'overfilled evaporator is also one of the inner tube type heat exchangers', but it flows through the inside of the tube as the target fluid, and on the shell side is the refrigerant. Since the overflow evaporator is provided with refrigerant to be vaporized above the evaporator casing, the liquid refrigerant is less likely to enter the inlet end of the compressor. • 2 = Since the full-type hair-expansion device soaks the tube in the liquid refrigerant in the evaporator housing, a large amount of liquid refrigerant is required, resulting in more than twice as much refrigerant filling as the direct-expansion evaporator. The amount will increase the cost of installation and environmental burden. 3 a Fig. 1 is a cross-sectional view showing a conventional spray evaporator 1〇1. As shown in Fig. 1, the shower evaporator 101 has a casing 1015, a shower 1011 disposed on the inner upper portion of the casing 1015, and a plurality of heats disposed in the horizontal direction below the Heralizer 1 Pass 丨〇丨3. After entering the inlet above the D leaner 1011, the liquid refrigerant is dripped down through the plurality of small holes (not shown) formed on the lower surface of the shower m to the underlying heat pipe 1013. The refrigerant film is formed on the surface of each of the heat transfer tubes 1013 by enriching the liquid refrigerant into the array of the heat transfer tubes 1013 arranged in a staggered manner, thereby performing heat exchange on the heat transfer tubes 1013. As indicated by the broken line in Fig. 1 'The evaporated refrigerant is discharged upward through the gap between the casing 101 5 and the shower 1 〇 11 . In addition, as disclosed in the Republic of China Patent No. M247805, the liquid refrigerant is dripped onto the heat transfer tube by means of an overflow tray and a shower tray, thereby achieving the effect of heat exchange. In addition, there are still US patents 5836382, 6167713, and 6686695 to change the structure of the shower to 6 19847 1320094 to achieve m!_ so that the liquid refrigerant can expand the effect of dripping on the heat pipe. Furthermore, U.S. Patent No. 5,904,807 utilizes the change of the upper structure of the evaporator to directly inject liquid refrigerant into the new spray structure to achieve the effect of expanding the spray. ▲ However, the above-mentioned spray evaporator is often configured such that the spray device allows the liquid refrigerant to drip over the heat transfer tube in a wide range, and the spray device is disposed farther from the refrigerant inlet above the evaporator. The position to obtain a larger spray area, but also allows the space within the evaporator to be configured with a heat transfer tube. Therefore, in order to achieve the desired heat exchange efficiency, the size of the evaporator housing must be relatively increased. Therefore, the conventional volcanic evaporating evaporator not only causes waste, but also increases the cost of materials and increases the cost of manufacturing. Q How to effectively solve the evaporation of the liquid refrigerant flowing from the top to the bottom in the prior art Developed a spray-type heat exchange device that does not need to increase the size when ===: ^^^The cost is reduced, or more than a few miles can be set in the same housing size, and the official spray heat The exchange device, in order to improve the heat exchange efficiency and avoid the bypass door, the area of the replacement, solve the problem, waste 'is the current cooling system, the content of the invention, the shortcomings of the prior art described above, The main object of the present invention is to improve the space-type (4) spray-type heat exchange shock, and another object is to provide a spray-type heat exchange device that uses the same number of heat transfer tubes while reducing its body gauge 19847. 7 1320094 is located in the embodiment: the shower unit is arranged to make it spray surface, and then. "The side is calculated from the position of 5 to 25% of the inner diameter of the casing. The heat transfer tubes of the two groups are set to take I:: the position on the side of the inner diameter of the casing. Thus, it is possible to obtain ', In another preferred embodiment, the shower unit is disposed on the lower side of the housing from the lower side of the housing to the gripped position J: the second group Between the heat transfer tube of the group and the heat transfer tube of the second group, a drip tray is disposed such that the disk surface is located at the lower side of the top of the housing and is about 2 〇 to a position of 〇%, between the heat transfer tubes of the two groups and the heat transfer tubes of the third group, the small drip tray is disposed such that the disk surface is located under the top of the housing The side calculation ^ is the position of 45 to 50% of the inner diameter of the body. Therefore, the heat transfer rate can be determined. In a preferred embodiment, the heat transfer tube is adjacent to the upper side. The following heat transfer tubes are staggered so as to flow through the heat pipes of the upper row and the refrigerant can be dripped through the heat pipes of the next column to the heat pipes of the other column. This 'can win the biggest The space utilization rate is more effective in arranging the heat transfer tubes in the heat exchange device. [Embodiment] Embodiments of the present invention will be described below with reference to the drawings. The drawings are simplified schematic diagrams and are merely illustrative of the present invention. The components of the invention, and the actual shape or size ratio of one piece are not characteristic of the present invention, but may be 19847 10 !32〇〇94
• I 進行變化’合先敘明。 式為本發明之第-實施例增 置二：:: 。如圖所示，喷淋式熱交換裝 ，並且在殼體中由上至下依序配置有 T #早70 Η、第一群組孰傳 群組熱傳管19。 滴淋盤π、以及第二 喷淋單元U之入口 111係連接於未圖式之 ·::=其喷淋面112形成有未圖式之複數個滴孔或； 用以使液態冷媒從該噴淋面112朝下方滴落。 1 ^ ·θ之尺寸、形狀及分佈等並無特別p艮制，只要能 二共給量，並且使液態冷媒能夠在噴淋面112 ;二：：滴落即可。滴孔或滴槽的形成位置則較宜對 二配置位置，以便使由滴孔或滴槽所滴落之冷 媒均此夠滴洛於相對應之熱傳管上。 傳管係包括複數支彼此平行配置的熱 c，寻熱傳管131之中係流動有欲進行s 體。相鄰上下列之該等熱傳管⑶係呈交錯配置。亦 之熱傳*131係配置在對應於上— =之間隙的位置。如此’可在相同之空 熱傳管131。 且又^ 、商淋：,7乂7之戴面係呈U字形而形成淺盤狀，且在該 = 質上整個盤面171係配置有複數個滴孔及/ 孔或、二以增進滴淋之面積及滴淋之均勾率。同樣地，滴 5㈢之尺寸、形狀及分佈等並無特別限制，只要能夠 19847 11 1320094 < Υ 配合冷媒之供給量，並且使液態冷媒能夠在盤面171之敖 面均句地滴落即可。滴孔或滴槽的形成位置則較宜對^ 熱傳管之配置位置，以便使由滴孔或滴槽所滴落之冷料 能夠滴落於相對應之熱傳管上。 q 第二群組熱傳管19係包括複數支彼此平行 傳官191。該等熱傳管191之中亦流動有欲進行冷卻之目 標流體。如同上述之第—群組熱傳管13，相鄰上下列之 戎等熱傳管191亦呈交錯配置。 • 卩下說明噴淋式熱交換裝置1的運作方式。首先，液 態冷媒由未圖式之供給源經由嗔淋單元n之入口⑴ 應至噴淋單元11後，經由形成於噴淋面U2之複數個滴 孔或滴槽而向下滴落。經滴落之液態冷媒會流經配置於噴 琳單元U下方之第-群組熱傳管13之各熱傳管i3i表貝 面，而與熱傳管131中所流動之目標流體進行熱交換，將 目標流體之熱量攜走，從而達成使目標流體冷卻之目的。 其次，流經第一群組熱傳管13之冷媒會接著滴落至 般盤17。由滴淋盤17所承接的冷媒’會先聚積在滴淋 ^中，然後再經由形成於盤面171中的滴孔或滴槽向 下j淋。經滴落之液態冷媒會流經配置於滴淋盤Η下方 之第二群组熱傳管19之各熱傳管191表面’而與熱傳管 崔中所々IL動之目；^流體進行熱交換，將目標流體之熱量 紅走，同樣達成使目標流體冷卻之目的。 、在接觸熱傳管m、191而進行熱交換的期間，一部 份之液態冷媒可能因為吸收熱量而被蒸發，而形成氣態冷 19847 12 ^20094 媒。此時’氣態冷媒會經由形成於滴淋盤17與殼體i 5 之間的間隙21、及形成於噴淋單元u與殼體15之間的 間隙20而向上竄升，並經由冷媒出口 151被回收以進 循環利用。 τ 1淋單元11與滴淋盤17之設置位置可以依據實際狀 =調整，以爭取熱交換裝置内的空間配置最大數量的熱傳 Β舉例而έ，當噴淋式熱交換裝置1之殼體15之截面 男' 貝上為圓環形，且假設該圓環形之内徑為D時，可將噴 •淋單it 11 &置在使喷淋面i i 2位於由殼體】5頂部下側算 起約5至25% D的位置’並將滴淋盤丨7設置在使盤面iη 位々、由敢體15頂部下側算起約4 〇 % D的位置。 I皆由本實施例之配置，由於毋須將喷淋單元設置在離 二乂換I置上方之冷媒入口較遠的位置亦能獲得廣大之 ΐ '麗面積且肖b夠在滴淋盤17及噴淋單元11之間配置熱 傳s，故旎夠充分利用蒸發器殼内之空間設置熱傳管，增 春進空間利科及熱傳效率，或是能夠在使用相同數量之熱 傳管的同時減小熱交換裝置本體之尺寸，俾減少生產製造 之成本。 以下芩照附圖說明未發明之其他實施例。在其他實施 例中，與第-實施例相同的元件係以相同之元件符號標 示’且不再進行詳細說明。 第3圖如為本發明之第二實施例之喷淋式熱交換裝 置的剖面示意圖。如圖所示，第二實施例之喷淋式熱交換 裝置2除了在殼體15中由上至下依序配置有喷淋單元 13 19847 1320094• I make changes. The formula is the second embodiment of the present invention:::. As shown in the figure, the spray type heat exchange unit is provided with T #早70 Η and the first group 孰 group heat transfer tube 19 in the housing from top to bottom. The drip tray π and the inlet 111 of the second shower unit U are connected to the following::= The shower surface 112 is formed with a plurality of drip holes of a pattern or not; The shower surface 112 is dropped downward. 1 ^ · The size, shape, and distribution of θ are not particularly limited, as long as the amount can be given in two, and the liquid refrigerant can be sprayed on the shower surface 112; The position at which the drip hole or the drip groove is formed is preferably disposed in such a position that the refrigerant dripped by the drip hole or the drip groove is sufficiently dripped on the corresponding heat transfer pipe. The pipe system includes a plurality of heats c arranged in parallel with each other, and the heat transfer pipe 131 has a flow to be s. The heat transfer tubes (3) adjacent to each other are arranged in a staggered configuration. Also, the heat transmission *131 is arranged at a position corresponding to the gap of the upper -=. Thus, the heat transfer tube 131 can be used in the same air. And ^, Shanglin:, 7乂7 wearing a U-shaped form to form a shallow dish, and in the quality of the entire disk surface 171 is equipped with a plurality of drops and / or two to enhance the drip The area and the average drop rate of dripping. Similarly, the size, shape, distribution, and the like of the droplets 5 (3) are not particularly limited as long as the supply amount of the refrigerant can be 19847 11 1320094 < Υ, and the liquid refrigerant can be uniformly dropped on the surface of the disk surface 171. The position at which the drip hole or the drip groove is formed is preferably disposed at a position where the heat transfer tube is disposed so that the cold material dripped by the drip hole or the drip groove can be dropped on the corresponding heat transfer tube. q The second group of heat transfer tubes 19 includes a plurality of branches parallel to each other. The target fluid to be cooled also flows through the heat transfer tubes 191. Like the above-mentioned group heat pipe 13, the heat transfer pipes 191 such as the cymbals adjacent to each other are also arranged in a staggered configuration. • The following describes how the spray heat exchanger 1 operates. First, the liquid refrigerant is dropped from the supply source (not shown) to the shower unit 11 via the inlet (1) of the shower unit n, and then dropped downward through a plurality of drip holes or drip grooves formed in the shower surface U2. The dripped liquid refrigerant flows through the surface of each heat transfer tube i3i disposed in the first group heat transfer tube 13 below the spray unit U, and exchanges heat with the target fluid flowing in the heat transfer tube 131. The heat of the target fluid is carried away to achieve the purpose of cooling the target fluid. Second, the refrigerant flowing through the first group of heat transfer tubes 13 is then dropped onto the tray 17. The refrigerant 'received by the drip tray 17 is first accumulated in the drip, and then poured down through the drip holes or drip grooves formed in the disc surface 171. The dripped liquid refrigerant will flow through the surface of each heat transfer tube 191 disposed in the second group of heat transfer tubes 19 below the drip tray, and move with the heat transfer tube Cuizhong. Exchange, the heat of the target fluid is red, and the purpose of cooling the target fluid is also achieved. During the heat exchange with the heat transfer tubes m, 191, a portion of the liquid refrigerant may be vaporized by absorbing heat to form a gaseous cold 19847 12 ^ 20094 medium. At this time, the "gaseous refrigerant" rises upward through the gap 21 formed between the drip tray 17 and the casing i 5 and the gap 20 formed between the shower unit u and the casing 15, and passes through the refrigerant outlet 151. It is recycled for recycling. The position of the τ 1 shower unit 11 and the drip tray 17 can be adjusted according to the actual shape = for the space arrangement in the heat exchange device to exemplify the maximum number of heat transfer έ, when the housing of the spray type heat exchange device 1 The cross section of the 15' male is a circular ring, and if the inner diameter of the circular ring is D, the spray can be placed on the top of the casing 5 The lower side counts the position of about 5 to 25% D and sets the drip tray 7 at a position where the disk surface iη is located at about 4 〇% D from the lower side of the top of the body. I is configured by the embodiment, because it is not necessary to set the shower unit at a position farther away from the refrigerant inlet above the second switch I can obtain the vast majority of the area, and the b is sufficient for the drip tray 17 and the spray. The heat transfer s is arranged between the shower unit 11, so that the heat transfer tube can be fully utilized in the space inside the evaporator shell to increase the space and the heat transfer efficiency, or to use the same number of heat transfer tubes. The size of the body of the heat exchange device is reduced, and the cost of manufacturing is reduced. Other embodiments not invented are described below with reference to the drawings. In other embodiments, the same components as those of the first embodiment are denoted by the same reference numerals and will not be described in detail. Figure 3 is a cross-sectional view showing a shower type heat exchange apparatus according to a second embodiment of the present invention. As shown in the figure, the shower type heat exchange device 2 of the second embodiment is provided with a shower unit in order from top to bottom in the housing 15 13 19847 1320094
* I 傳管13、二個滴淋盤…、…及 置另一個19外，還另外在第二群組熱傳管19下配 、個滴淋i 23、以及第三群組熱傳管25。 滴淋截面係^字形而形成淺盤狀，且在該 或滴柙。同i整個盤面231亦配置有複數個滴孔及/ 特別；制。，滴孔或滴槽之尺寸、形狀及分佈等並無 "句在 '9 配合冷媒之供給量，並且使液態冷媒 月匕夠在盤面2 31之暫面於4从、电β …w ㈣可。滴孔或滴槽的形 ==對應於熱傳管之配置位置’以便使由滴孔或 "滴洛之冷媒均能夠滴落於相對應之敎傳管上。 ，三群組熱傳管25係包括複數支彼此平行配置的熱 2吕5卜該等熱傳管251之中亦流動有欲進行冷卻之目 標流體。同樣地，相鄰上下列之該等熱傳管25ι亦呈交錯 酉己置。 …在本實施例中，由於設置二層之滴淋盤，並且將熱傳 •I分成ί組來配置’因此能夠更有彈性地依據實際狀況調 主贺淋单元、料盤及熱傳管的配置方<，以爭取在熱交 換裝置内的空間中g己置最大數量的熱傳I。舉例而言，當 噴淋式熱交換裝置2之殼體15之截面實質上為圓_，田 且假設該圓環形之内徑為！>時，可將噴淋單元η設置在 使喷淋面112位於由殼體15頂部下側算起約5至25% D 的位置，將滴淋盤17-1及17-2設置在使其盤面171^ 及171-2位於由殼體15頂部下側算起約2〇至3〇%d的位 置’並將滴淋盤23設置在使其盤面231位於由殼體15 19847 14 1320094* I tube 13, two drip trays ..., ... and another 19, in addition to the second group of heat transfer tubes 19, a drip i 23, and a third group of heat transfer tubes 25 . The drip section is in the shape of a chevron to form a shallow disc shape, and is in the drip. The same disk surface 231 is also provided with a plurality of drop holes and / special; The size, shape and distribution of the drip hole or drip groove are not in the sentence of '9 with the supply of refrigerant, and the liquid refrigerant is enough for the face of the disk 2 to be 4, and the electricity is β...w (4) can. The shape of the drip hole or the drip groove == corresponds to the arrangement position of the heat transfer tube so that the drip hole or the refrigerant of the drip can be dripped on the corresponding turbulent pipe. The three-group heat transfer tube 25 includes a plurality of heats arranged in parallel with each other. The heat transfer tubes 251 also have a target fluid to be cooled. Similarly, the heat transfer tubes 25ι adjacent to each other are also staggered. ...in this embodiment, since the two-layer drip tray is provided, and the heat transfer I is divided into groups, the configuration can be configured to adjust the main shower unit, the tray and the heat transfer tube more flexibly according to the actual situation. The configuration side <, in order to obtain the maximum number of heat transfer I in the space inside the heat exchange device. For example, when the housing 15 of the shower heat exchange device 2 has a substantially circular cross section, it is assumed that the inner diameter of the circular ring is! >, the shower unit η may be disposed such that the shower surface 112 is located at a position of about 5 to 25% D from the lower side of the top of the casing 15, and the drip trays 17-1 and 17-2 are disposed such that The disk faces 171 and 171-2 are located at a position of about 2 〇 to 3 〇 % d from the lower side of the top of the housing 15 and the drip tray 23 is placed such that the disk surface 231 is located by the housing 15 19847 14 1320094
< I 頂部下側算起約45至50%D的位置。 再者，在本實施例中，由於形成二個滴淋盤丨^、 17-2’並在該等滴淋盤丨了 —丨、17_2之間形成有間隙Η，， 故能夠使已被蒸發之氣態冷媒更順暢地向上竄升，而更有 ， 效率地回收冷媒以進行循環利用。 . 雖然在本實施例中，係以設置二層之滴淋盤為例進行 說明，但本發明亦可經由增設更多層之滴淋盤達到多次承 接剩餘液態冷媒之效，並不以設置二層之滴淋盤為限。 鲁、苐4圖奋藏示本發明弟一實施例之一變化例之噴淋 ^熱交換裝置的剖面示意圖。如圖所示，本變化例之噴淋 、式熱交換裝置3中的滴淋盤Π之週壁係朝外側傾斜，從 而能夠更大範圍地承接由上方滴落之冷媒。 1 '第5圖係顯示本發明第二實施例之一變化例之喷淋 式熱交換裝置的剖面示意圖。如圖所示，本變化例之噴淋 式熱交換裝置4中的滴淋盤17-1，、17-2,、23,之截面係 鲁呈開口朝上之圓滑曲線狀，從而亦能夠大範圍地承接由上 方滴落之冷媒。此外，藉由構成此種形狀，滴淋盤中亦較 ' 不易形成使冷媒聚積無法滴落的死角。 • 上述實施例配合附圖僅例示性說明本發明之原理及 其功效，而非用於限制本發明。任何熟習此項技藝之人士 均可在不違背本發明之精神及範疇下，對上述實施例進行 修飾與㈣。因& ’本發明之權利保護範圍，應如後述之 申s月專利範圍所列。 【圖式簡單說明】 19847 15 1320094< I The position on the lower side of the top is about 45 to 50% D. Furthermore, in the present embodiment, since two drip trays 、^, 17-2' are formed and a gap 形成 is formed between the drip trays, 丨, 17_2, it is possible to evaporate The gaseous refrigerant is more smoothly swelled up, and more efficiently, the refrigerant is recovered for recycling. Although in the present embodiment, the two-layer drip tray is taken as an example for description, the present invention can also achieve the effect of receiving the remaining liquid refrigerant multiple times by adding more layers of drip trays, and is not set. The second layer of drip tray is limited. Lu and Lu 4 show a schematic cross-sectional view of a shower heat exchange device according to a variation of one embodiment of the present invention. As shown in the figure, the peripheral wall of the drip tray in the shower type heat exchange device 3 of the present modification is inclined outward, so that the refrigerant dripped from above can be received in a wider range. 1 ' Fig. 5 is a schematic cross-sectional view showing a shower type heat exchange device according to a variation of the second embodiment of the present invention. As shown in the figure, in the spray type heat exchange device 4 of the present modification, the drip trays 17-1, 17-2, and 23 have a rounded curved shape with an opening upward, and thus can also be large. The range of the refrigerant dripping from above is taken. Further, by constituting such a shape, the drip tray is also less likely to form a dead angle which prevents the refrigerant from accumulating. The above embodiments are merely illustrative of the principles of the invention and its advantages, and are not intended to limit the invention. Any of the above-described embodiments may be modified and (4) by those skilled in the art without departing from the spirit and scope of the invention. The scope of the rights of the present invention should be as set forth in the scope of the patent application. [Simple description of the map] 19847 15 1320094
令 I 第1圖係顯示習知之噴淋式蒸發器101之剖視圖； 第2圖係為本發明之第〆實施例之噴淋式熱交換裝 置的剖面示意圖； 第3圖係為本發明之第二實施例之噴淋式熱交換裝 置的剖面示意圖； 第4圖係顯示本發明第一實施例之一變化例之喷淋 式熱父換裝置的剖面示意圖；以及 第5圖係顯示本發明第二實施例之一變化例之喷淋 鲁式熱父換裝置的剖面示意圖。 【主要元件符號說明 1、2、3、4、101 1011 11 131 、 191 、 251 、 1013 13 19 ’25 20 、 21 、 21’ 、 22 111 112 151 噴淋式熱交換裝置 噴淋器 噴淋單元 熱傳管 第一群組熱傳管 第二群組熱傳管 第三群組熱傳管 間隙 冷媒入口 噴淋面 冷媒出口 17、Π’、Π-1、17-2、Π-1，、17一2，滴淋盤 171 ' 171-1 ' 171-2 盤面 15 ' 1015 殼體 16 198471 is a cross-sectional view showing a conventional spray evaporator 101; FIG. 2 is a schematic cross-sectional view showing a spray type heat exchange device according to a third embodiment of the present invention; 2 is a schematic cross-sectional view of a shower type heat exchange device according to a variation of the first embodiment of the present invention; and FIG. 5 is a cross-sectional view showing the spray type heat master device of the first embodiment of the present invention; A schematic cross-sectional view of a sprayed Lu hot father changing device in a variation of the second embodiment. [Main component symbol description 1, 2, 3, 4, 101 1011 11 131 , 191 , 251 , 1013 13 19 '25 20 , 21 , 21 ' , 22 111 112 151 Spray type heat exchanger sprinkler shower unit Heat pipe first group heat pipe second group heat pipe third group heat pipe gap refrigerant inlet shower face refrigerant outlet 17, Π', Π-1, 17-2, Π-1, 17-2, drip tray 171 ' 171-1 ' 171-2 panel 15 ' 1015 housing 16 19847