TWI663371B - Evaporator structure - Google Patents
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- TWI663371B TWI663371B TW107133405A TW107133405A TWI663371B TW I663371 B TWI663371 B TW I663371B TW 107133405 A TW107133405 A TW 107133405A TW 107133405 A TW107133405 A TW 107133405A TW I663371 B TWI663371 B TW I663371B
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Abstract
一種蒸發器結構，係包含有一熱交換元件、一導熱外殼及一上蓋，其中該熱交換元件設置於該導熱外殼中，該上蓋係覆蓋於導熱外殼上，以將熱交換元件封閉，該熱交換元件上具有複數條的橫向通道，並於下方兩側分別開設一第一縱向冷卻流體通道，接近中央區設置有複數條長度較短的一第二縱向冷卻流體通道，當導熱外殼接受熱源時，該冷卻流體會經由橫向通道朝二側的第一縱向冷卻流體通道流動，經由該縱向第一冷卻流體通道及橫向通道導引，使冷卻流體可朝第二縱向冷卻流體通道流動，將冷卻流體均勻帶入熱源區，達到全面積散熱之目的。 An evaporator structure includes a heat exchange element, a heat conductive shell, and an upper cover, wherein the heat exchange element is disposed in the heat conductive shell, and the upper cover covers the heat conductive shell to close the heat exchange element, and the heat exchange The element has a plurality of lateral channels, and a first longitudinal cooling fluid channel is opened on each of the lower sides. A plurality of second longitudinal cooling fluid channels with a shorter length are provided near the central area. When the heat-conducting shell receives a heat source, The cooling fluid flows through the lateral channel toward the first longitudinal cooling fluid channel on both sides, and is guided through the longitudinal first cooling fluid channel and the lateral channel, so that the cooling fluid can flow toward the second longitudinal cooling fluid channel and uniform the cooling fluid. Bring it into the heat source area, to achieve the purpose of full area heat dissipation.
Description
本發明是有關一種蒸發器結構，係得讓冷卻流體於內部進行液、氣轉換，並經由特殊水通道設計，達到全面性散熱之目的。 The invention relates to an evaporator structure, which is to allow the cooling fluid to perform liquid-gas conversion inside, and to achieve the purpose of comprehensive heat dissipation through a special water channel design.
近年來熱源產生裝置的發熱量隨著半導體製程的精進而不斷的快速升高；如何提升熱源產生裝置的散熱能力，維護元件之正常運作，遂成為一項非常重要的工程課題。目前大量使用的直接空氣冷卻技術已經無法滿足許多具有高熱通量熱源產生裝置散熱的需求，而必須尋求其他的解決方案。 In recent years, the heat generation of the heat source generating device has been increasing rapidly with the refinement of the semiconductor process; how to improve the heat dissipation capacity of the heat source generating device and maintain the normal operation of the components has become a very important engineering issue. At present, the direct air cooling technology that is widely used has been unable to meet the demand for heat dissipation of many heat generating devices with high heat flux, and other solutions must be sought.
現有之技術中，除了透過空氣冷卻技術之外，具有利用冷卻流體的液、氣轉換達到散熱效果，此一技術係提供兩組均熱器及兩組連通之管體，一組均熱器用以蒸發來帶走所吸收之熱量，另一組均熱器用以冷凝以降溫來返回輸出冷卻冷卻流體進行散熱循環之迴路，而兩組均熱器內的壓力不同，故可讓冷卻流體自動進行往返輸送，但所述均熱器其內部大多只是簡單的鰭片或通道設計以供冷卻流體於其中流通，容易造成熱源集中於特定位置，故在特定位置則會產生因過盛的蒸發水位過低、局部位置高溫的狀態，不僅致使散熱效果不穩定、不均勻，更快速減少使用壽命。 In the existing technology, in addition to the air cooling technology, the liquid and gas conversion of the cooling fluid is used to achieve the heat dissipation effect. This technology provides two sets of heat equalizers and two sets of connected pipe bodies. One set of heat equalizers is used to Evaporation to take away the absorbed heat, another set of heat equalizers is used to condense to reduce the temperature to return the output cooling cooling fluid for the heat dissipation cycle. The pressure in the two sets of heat equalizers is different, so the cooling fluid can automatically go back and forth. Conveying, but most of the homogenizers are simply fins or channels designed for cooling fluid to circulate in the homogenizer, which easily causes the heat source to be concentrated in a specific location, so the excessive evaporation water level at a specific location will be too low. The high temperature in the local location not only causes the heat dissipation effect to be unstable and uneven, but also reduces the service life more quickly.
一種蒸發器結構，係至少包含：一熱交換元件，該熱交換元件可區分成一蒸氣區及一進水區，且該蒸氣區及該進水區之間處具有一阻隔牆，該 熱交換元件內部形成有複數條相互平行且上下貫穿的橫向通道，並於該進水區上方接近中央處開設有一縱向進水上通道，該蒸氣區上方接近中央處開設複數個縱向蒸氣通道，藉由該阻隔牆的設置，使該縱向進水上通道及該縱向蒸氣通道之間彼此互不相通，且該縱向進水上通道及該縱向蒸氣通道係與該橫向通道相互垂直設置，該熱交換元件下方接近兩側邊緣分別開設一第一縱向冷卻流體通道，該第一縱向冷卻流體通道係貫穿該蒸氣區、該進水區及該阻隔牆下方，使該第一縱向冷卻流體通道貫穿該熱交換元件的二端緣，而該蒸氣區下方接近中央處設置有複數條第二縱向冷卻流體通道，該第二縱向冷卻流體通道的長度由一側至阻隔牆，使第二縱向冷卻流體通道的長度與該縱向蒸氣通道相同，與該縱向進水上通道也經由阻隔牆的阻擋，而與該進水區彼此不相連通，該第二縱向冷卻流體通道長度短於第一縱向冷卻流體通道，且該第二縱向冷卻流體通道與該縱向蒸氣通道的設置位置錯開；一導熱外殼，該導熱外殼內部用於置放該熱交換元件；一上蓋，係用於遮蓋在該導熱外殼上方，該上蓋上分別開設有一蒸氣出口與一入水口，且該蒸氣出口係對應於該蒸氣通道位置上方，該入水口則係對應於其中一個該縱向進水上通道位置上方。 An evaporator structure includes at least: a heat exchange element, the heat exchange element can be divided into a steam area and a water inlet area, and a barrier wall is provided between the steam area and the water inlet area. A plurality of horizontal channels running parallel to each other and penetrating vertically are formed inside the heat exchange element, and a longitudinal water inlet channel is set near the center above the water inlet area, and a plurality of vertical steam channels are set near the center above the steam area. The barrier wall is arranged so that the longitudinal water inlet channel and the longitudinal steam channel are not connected with each other, and the longitudinal water inlet channel and the longitudinal steam channel are arranged perpendicular to the lateral channel, and the heat exchange element is close to the bottom. A first longitudinal cooling fluid channel is opened on each side edge, and the first longitudinal cooling fluid channel runs through the vapor region, the water inlet region and under the barrier wall, so that the first longitudinal cooling fluid channel passes through the heat exchange element. Two end edges, and a plurality of second longitudinal cooling fluid channels are arranged near the center below the vapor zone, and the length of the second longitudinal cooling fluid channels is from one side to the barrier wall, so that the length of the second longitudinal cooling fluid channels is equal to the The longitudinal steam channel is the same, and the longitudinal water inlet channel is also blocked by the barrier wall, and it is not the same as the water inlet area. The second longitudinal cooling fluid channel is shorter than the first longitudinal cooling fluid channel, and the second longitudinal cooling fluid channel is staggered from the setting position of the longitudinal vapor channel; a heat conducting shell, the inside of the heat conducting shell is used for placing the A heat exchange element; an upper cover is used to cover the heat conductive shell, and a steam outlet and a water inlet are respectively provided on the upper cover, and the steam outlet corresponds to the position of the steam channel, and the water inlet corresponds to One of the longitudinal inlet channels is above the position.
於一較佳實施例中，其中該熱交換元件為一體成型。 In a preferred embodiment, the heat exchange element is integrally formed.
於一較佳實施例中，該蒸氣區的面積大於進水區，該縱向進水上通道長度由一側至該阻隔牆，該縱向蒸氣通道的長度由一側至該阻隔牆，使該縱向蒸氣通道長度大於該縱向進水上通道 In a preferred embodiment, the area of the steam area is larger than that of the water inlet area, the length of the longitudinal water inlet channel is from one side to the barrier wall, and the length of the vertical steam channel is from one side to the barrier wall, so that the longitudinal steam The length of the channel is longer than the longitudinal inlet channel
如於一較佳實施例中，其中該熱交換元件的該縱向蒸氣通道與該第二縱向冷卻流體通道的長度相同。 As in a preferred embodiment, the length of the longitudinal vapor passage of the heat exchange element and the second longitudinal cooling fluid passage are the same.
於一較佳實施例中，其中該縱向蒸氣通道位於該蒸氣區接近中央 處，且長度由一側邊緣至阻隔牆，且該縱向進水上通道長度由一側邊緣至阻隔牆，使該熱交換元件的該縱向蒸氣通道與第二縱向冷卻流體通道藉由阻隔牆的阻擋，彼此不相連通。 In a preferred embodiment, the longitudinal vapor channel is located near the center of the vapor region. And the length from one side edge to the barrier wall, and the length of the longitudinal water inlet channel from the side edge to the barrier wall, so that the longitudinal vapor channel and the second longitudinal cooling fluid channel of the heat exchange element are blocked by the barrier wall , Are not connected to each other.
於一較佳實施例中，其中該第二縱向冷卻流體通道位於該蒸氣區接近中央處，且長度由一側邊緣至阻隔牆，且該縱向進水上通道長度由一側邊緣至阻隔牆，使該熱交換元件的蒸氣通道與第二縱向冷卻流體通道藉由阻隔牆的阻擋，彼此不相連通。 In a preferred embodiment, the second longitudinal cooling fluid channel is located near the center of the vapor zone and has a length from one side edge to the barrier wall, and the length of the longitudinal water inlet channel from one side edge to the barrier wall, so that The vapor channel of the heat exchange element and the second longitudinal cooling fluid channel are not connected to each other by the blocking wall.
1‧‧‧熱交換元件 1‧‧‧ heat exchange element
11‧‧‧蒸氣區 11‧‧‧Steam Zone
12‧‧‧進水區 12‧‧‧Water intake area
13‧‧‧阻擋牆 13‧‧‧ barrier wall
14‧‧‧橫向通道 14‧‧‧ horizontal passage
15‧‧‧縱向進水上通道 15‧‧‧ Longitudinal waterway
16‧‧‧縱向蒸氣通道 16‧‧‧longitudinal vapor channel
17‧‧‧第一縱向冷卻流體通道 17‧‧‧ the first longitudinal cooling fluid channel
18‧‧‧第二縱向冷卻流體通道 18‧‧‧ second longitudinal cooling fluid channel
2‧‧‧導熱外殼 2‧‧‧ Thermally conductive housing
3‧‧‧上蓋 3‧‧‧ Upper cover
31‧‧‧蒸氣出口 31‧‧‧Steam Outlet
32‧‧‧入水口 32‧‧‧ Inlet
4‧‧‧熱源產生裝置 4‧‧‧ heat source generator
5‧‧‧散熱鰭片 5‧‧‧Heat fins
6‧‧‧蒸氣通管 6‧‧‧Steam tube
7‧‧‧冷卻流體通管 7‧‧‧Cooling fluid pipe
8‧‧‧冷凝器 8‧‧‧ condenser
A‧‧‧冷卻流體 A‧‧‧ cooling fluid
B‧‧‧蒸氣體 B‧‧‧Steam
[第1圖]係本發明蒸發器結構之分解結構立體示意圖。 [FIG. 1] It is a three-dimensional schematic diagram of the exploded structure of the evaporator structure of the present invention.
[第2圖]係本發明蒸發器結構之熱交換元件另一視角立體示意圖。 [Figure 2] A perspective view of the heat exchange element of the evaporator structure of the present invention from another perspective.
[第3圖]係本發明蒸發器結構之結構剖面示意圖 [Figure 3] Schematic sectional view of the structure of the evaporator of the present invention
[第4圖]係本發明蒸發器結構之實施冷卻流體氣態流動剖面示意圖。 [Fig. 4] It is a schematic sectional view showing the gaseous flow of the cooling fluid during the implementation of the evaporator structure of the present invention.
[第5圖]係本發明蒸發器結構結合冷凝器使用之立體外觀示意圖。 [Fig. 5] It is a schematic diagram of the three-dimensional appearance of the evaporator structure combined with the condenser of the present invention.
[第6圖]係本發明蒸發器結構之實施冷卻流體液態流動剖面示意圖。 [Fig. 6] A schematic sectional view of the liquid flow of the cooling fluid during the implementation of the evaporator structure of the present invention.
[第7圖]係本發明蒸發器結構之實施冷卻流體液態流動平面示意圖。 [FIG. 7] It is a schematic plan view of the liquid flow of the cooling fluid in the evaporator structure of the present invention.
有關於本發明其他技術內容、特點與功效，在以下配合參考圖式之較佳實施例的詳細說明中，將可清楚的呈現。 Regarding other technical contents, features and effects of the present invention, they will be clearly presented in the following detailed description of the preferred embodiments with reference to the drawings.
請參閱第1~3圖，為本發明蒸發器結構之分解結構示意圖及另一視角的立體示意圖，其中該蒸發器結構係包含一熱交換元件1、一導熱外殼2、一上蓋3； 其中該熱交換元件1可為一體成型或組裝而成，該熱交換元件1可區分成一蒸氣區11及一進水區12，該蒸氣區11的面積大於進水區12，且該蒸氣區11及該進水區12之間處具有一阻隔牆13，該熱交換元件1內部形成有複數條相互平行且上下貫穿的橫向通道14，並於該進水區12上方接近中央處開設有一縱向進水上通道15，該縱向進水上通道15長度由一側至該阻隔牆13，該蒸氣區11上方接近中央處開設複數個縱向蒸氣通道16(在本實施例中該縱向進水上通道15設有一道、該縱向蒸氣通道16設有三道)，該縱向蒸氣通道16的長度由一側至該阻隔牆13，使該縱向蒸氣通道16長度大於該縱向進水上通道15，藉由該阻隔牆13的設置，使該縱向進水上通道15及該縱向蒸氣通道16之間彼此互不相通，且該縱向進水上通道15及該縱向蒸氣通道16係與該橫向通道14相互垂直設置；該熱交換元件1下方接近兩側邊緣分別開設一第一縱向冷卻流體通道17，該第一縱向冷卻流體通道17係貫穿該蒸氣區11、該進水區12及該阻隔牆13下方，使該第一縱向冷卻流體通道17貫穿該熱交換元件1的二端緣，而該蒸氣區11下方接近中央處設置有複數條第二縱向冷卻流體通道18，該第二縱向冷卻流體通道18的長度由一側至阻隔牆13，使第二縱向冷卻流體通道18的長度與該縱向蒸氣通道16相同，與該縱向進水上通道15也經由阻隔牆13的阻擋，而與該進水區12彼此不相連通(在本實施例中該第二縱向冷卻流體通道18設有四道、該第一縱向冷卻流體通道17設有二道)，且該第二縱向冷卻流體通道18與該縱向蒸氣通道16的設置位置錯開；其中該導熱外殼2內部用於置放該熱交換元件1；其中該上蓋3係用於遮蓋在該導熱外殼2上方，該上蓋3上分別開設 有一蒸氣出口31與一入水口32，且該蒸氣出口31係對應於其中一個該縱向蒸氣通道16位置上方，該入水口32則係對應於其中該縱向進水上通道15位置上方。 Please refer to FIGS. 1 to 3, which are schematic diagrams of an exploded structure of the evaporator structure of the present invention and a perspective view from another perspective. The evaporator structure includes a heat exchange element 1, a thermally conductive housing 2, and an upper cover 3. The heat exchange element 1 can be integrally formed or assembled. The heat exchange element 1 can be divided into a steam area 11 and a water inlet area 12. The area of the steam area 11 is larger than the water inlet area 12 and the steam area 11. There is a blocking wall 13 between the water inlet area 12 and the heat exchange element 1. A plurality of horizontal channels 14 parallel to each other and penetrating up and down are formed in the heat exchange element 1. A vertical inlet is provided near the center above the water inlet area 12. Water channel 15, the length of the longitudinal water channel 15 from one side to the barrier wall 13, a plurality of vertical steam channels 16 are opened above the steam area 11 near the center (in this embodiment, one channel is provided for the longitudinal water channel 15). There are three longitudinal steam channels 16), and the length of the longitudinal steam channel 16 is from one side to the barrier wall 13 so that the length of the longitudinal steam channel 16 is longer than the longitudinal water inlet channel 15 by the arrangement of the barrier wall 13 So that the longitudinal water inlet channel 15 and the longitudinal steam channel 16 are not connected with each other, and the longitudinal water inlet channel 15 and the longitudinal steam channel 16 are arranged perpendicular to the lateral channel 14; below the heat exchange element 1 A first longitudinal cooling fluid channel 17 is respectively opened near the edges of both sides, and the first longitudinal cooling fluid channel 17 runs through the vapor region 11, the water inlet region 12, and the barrier wall 13 to make the first longitudinal cooling fluid channel 17 17 runs through the two end edges of the heat exchange element 1, and a plurality of second longitudinal cooling fluid passages 18 are provided near the center below the vapor zone 11, and the length of the second longitudinal cooling fluid passages 18 is from one side to the barrier wall 13 So that the length of the second vertical cooling fluid channel 18 is the same as the length of the vertical vapor channel 16 and the vertical water inlet channel 15 is also blocked by the barrier wall 13 and is not connected to the water inlet area 12 (in this embodiment) The second longitudinal cooling fluid channel 18 is provided with four channels, and the first longitudinal cooling fluid channel 17 is provided with two channels), and the second longitudinal cooling fluid channel 18 and the longitudinal vapor channel 16 are disposed staggered; The heat-conducting shell 2 is used for placing the heat-exchange element 1 inside; the upper cover 3 is used to cover the heat-conducting shell 2, and the upper covers 3 are respectively opened. There is a steam outlet 31 and a water inlet 32, and the steam outlet 31 corresponds to a position above one of the longitudinal steam channels 16, and the water inlet 32 corresponds to a position above the longitudinal water inlet channel 15.
在一般情況下，各該導熱外殼2中具有一預定量的冷卻流體A以及蒸氣體B，如第4、5圖所示，而實施使用時，該導熱外殼2底面係固定於一熱源產生裝置4上，該熱源產生裝置4會與該熱交換元件1的蒸氣區相對應，並可於該上蓋3上一併裝設有一散熱鰭片5、一蒸氣通管6及一冷卻流體通管7，該蒸氣通管6及一冷卻流體通管又連結一冷凝器8，當該熱源產生裝置4產生熱源時，該熱源產生裝置4所產生的熱能能夠導入該導熱外殼2內部產生熱源區至該熱交換元件1之蒸氣區11，當該導熱外殼2接收到的熱源達到一預定的蒸發溫度時，該位於熱交換元件1之橫向通道14及第二縱向冷卻流體通道18內的冷卻流體A即會因高溫而蒸發成蒸氣體B，該蒸氣體B會經由該橫向通道14導引並上升匯流至該數條縱向蒸氣通道16，經由數條縱向蒸氣通道16洩壓，避免該導熱外殼2內部壓力過於集中，而該蒸氣體B會經由該蒸氣出口31及該蒸氣通管6傳送至該冷凝器8，經由該冷凝器8降溫後會將該蒸氣體B轉換成該冷卻流體A，而由於該冷卻流體A蒸發成氣態進入該冷凝器8後，該熱交換元件1內壓力變小，使得進入該冷凝器8變成的冷卻流體A，得再經由該冷卻流體通管7回流回蒸發器的該熱交換元件1；之後，如第4、6、7圖所示，該冷卻流體A回流會依序通過入水口32、縱向進水上通道15而進入各橫向通道14，由於該第二縱向冷卻流體通道18未與該縱向進水上通道15相連通，因此，當冷卻流體A經由縱向進水上通道15流入時，該冷卻流體A會經由橫向通道14分別往兩側方向流動，再經由該第一縱向冷卻流體通道17導引而做縱向流動，然後，在藉由該橫向通道14往第二縱向冷卻流體通道18流動，藉由第二縱向冷卻流體通道18的設置，使冷卻流體A可朝 該熱源產生裝置4所產生的熱源區的橫向位置及縱向位置流動，以將大量冷卻流體A傳送熱源區，避免冷卻流體A因入量太少，而發生冷卻不及，造成溫度及壓力大幅提升，因此，藉由該第一縱向冷卻流體通道17及該第二縱向冷卻流體通道18的設置，可將冷卻流體A由最外側帶入中央的熱源區，使熱交換元件的每個位置都會與該冷卻流體A接觸，達到散熱的目的，而冷卻流體A進入熱源區時，會再次受熱蒸發成蒸氣體B，並得向上通過蒸氣通道13以及蒸氣出口31依序進入通管6至冷凝器8，以此不斷循環，以達到循環散熱之目的；經此，可知冷卻流體A於該熱交換元件1的蒸氣區11受熱蒸發成蒸氣體B，進而將熱帶離傳送至該冷凝器8，經由冷凝結成冷卻流體A則又回流至該熱交換元件1的進水區12，由於該進水區12與該蒸氣區11之間具有一阻隔牆13，因此可讓冷卻流體A與蒸氣體B於該熱交換元件1中各別作用，達到氣液分離、冷熱交替與自動循環的功效。 In general, each of the heat-conducting shells 2 has a predetermined amount of cooling fluid A and vapor body B, as shown in Figs. 4 and 5, and when used, the bottom surface of the heat-conducting shell 2 is fixed to a heat source generating device. 4, the heat source generating device 4 will correspond to the vapor region of the heat exchange element 1, and a heat dissipation fin 5, a vapor duct 6 and a cooling fluid duct 7 can be installed on the upper cover 3 together. The steam pipe 6 and a cooling fluid pipe are connected to a condenser 8. When the heat source generating device 4 generates a heat source, the heat energy generated by the heat source generating device 4 can be introduced into the heat conducting housing 2 to generate a heat source region to the heat source area. In the vapor zone 11 of the heat exchange element 1, when the heat source received by the thermally conductive housing 2 reaches a predetermined evaporation temperature, the cooling fluid A located in the lateral passage 14 and the second longitudinal cooling fluid passage 18 of the heat exchange element 1 is It will evaporate into the vapor body B due to the high temperature. The vapor body B will be guided through the lateral channel 14 and rise and converge to the plurality of longitudinal vapor channels 16, and release the pressure through the plurality of longitudinal vapor channels 16 to avoid the inside of the thermally conductive housing 2. Stress is too concentrated The vapor body B will be transmitted to the condenser 8 through the vapor outlet 31 and the vapor vent pipe 6. After the temperature of the condenser 8 is reduced, the vapor body B will be converted into the cooling fluid A, and because the cooling fluid After A evaporates into a gaseous state and enters the condenser 8, the pressure in the heat exchange element 1 becomes smaller, so that the cooling fluid A entering the condenser 8 becomes a heat exchange that must be returned to the evaporator via the cooling fluid passage pipe 7 Element 1; afterwards, as shown in FIGS. 4, 6, and 7, the return flow of the cooling fluid A will sequentially pass through the water inlet 32, the longitudinal water inlet channel 15 and enter each of the lateral channels 14, because the second longitudinal cooling fluid channel 18 It is not in communication with the longitudinal water inlet channel 15. Therefore, when the cooling fluid A flows in through the longitudinal water inlet channel 15, the cooling fluid A flows to both sides through the lateral channel 14 and then through the first longitudinal cooling fluid. The channel 17 is guided for longitudinal flow, and then flows through the lateral channel 14 to the second longitudinal cooling fluid channel 18, and the cooling fluid A can be directed toward The heat source area generated by the heat source generating device 4 flows in a horizontal position and a vertical position to transfer a large amount of cooling fluid A to the heat source area, to prevent the cooling fluid A from being cooled too much due to the inflow of too little, resulting in a significant increase in temperature and pressure. Therefore, with the arrangement of the first longitudinal cooling fluid passage 17 and the second longitudinal cooling fluid passage 18, the cooling fluid A can be brought into the central heat source region from the outermost side, so that each position of the heat exchange element will be related to the The cooling fluid A comes into contact to achieve the purpose of heat dissipation, and when the cooling fluid A enters the heat source area, it will be heated and evaporated again into the vapor body B, and it must pass through the vapor passage 13 and the vapor outlet 31 to enter the through pipe 6 to the condenser 8 in sequence. This keeps circulating to achieve the purpose of circulating heat; after this, it can be seen that the cooling fluid A is heated to evaporate into the vapor body B in the vapor zone 11 of the heat exchange element 1, and then the tropical heat is transferred to the condenser 8 and formed through condensation. The cooling fluid A flows back to the water inlet area 12 of the heat exchange element 1. Since a barrier wall 13 is provided between the water inlet area 12 and the vapor area 11, the cooling fluid A and the steam The gas B plays a respective role in the heat exchange element 1 to achieve the effects of gas-liquid separation, cold-heat alternation and automatic circulation.
另外，如第5圖所示，由於該第二縱向冷卻流體通道18與該蒸氣通道13的設置位置錯開，因此，可增加冷卻流體A在各該橫向通道14內流竄的面積，進而提升散熱的效益。 In addition, as shown in FIG. 5, since the installation positions of the second longitudinal cooling fluid passage 18 and the vapor passage 13 are staggered, the area through which the cooling fluid A flows in each of the transverse passages 14 can be increased, thereby improving the heat dissipation. benefit.
本發明所提供之蒸發器結構，係特別改良了熱交換元件內冷卻流體通道的配置進而改善冷卻流體於內部流通的路徑，以提升整體散熱效益，其優點如下： The evaporator structure provided by the present invention particularly improves the configuration of the cooling fluid channel in the heat exchange element, thereby improving the path of the cooling fluid flowing in the interior, so as to improve the overall heat dissipation benefit. The advantages are as follows:
1.本發明提供的熱交換元件，係特別分設進水區及蒸氣區，並只有第一縱向冷卻流體通道可連通進水區及蒸氣區，因此，在冷卻流體進入縱向進水上通道後必須強制的被導往兩側方向流動，再經由橫向通道將冷卻流體導引至第二縱向冷卻流體通道回流至該熱交換元件的蒸氣區，使冷卻 流體會均勻的流遍整個熱交換元件的進水區及蒸氣區，讓冷卻流體以最大的接觸面積於熱交換元件內流動循環，因此具有提升整體散熱效益的全面積散熱。 1. The heat exchange element provided by the present invention is specially divided into a water inlet area and a steam area, and only the first longitudinal cooling fluid channel can communicate with the water inlet area and the steam area. Therefore, after the cooling fluid enters the longitudinal water inlet upper channel, it must be It is forced to flow in both directions, and then the cooling fluid is guided to the second longitudinal cooling fluid channel through the lateral channel to return to the vapor region of the heat exchange element to cool The fluid will evenly flow through the water inlet area and steam area of the entire heat exchange element, allowing the cooling fluid to circulate in the heat exchange element with the largest contact area, so it has a full area heat dissipation that improves the overall heat dissipation efficiency.
2.本發明提供的熱交換元件，係特別將該蒸氣區下方位置處設置有複數條的第二縱向冷卻流體通道，各通道之間因為數量增多而減短間距，因此，可均衡冷卻流體在各第二縱向冷卻流體通道之間的水位，避免有特定位置水位過低而造成局部位置高溫的狀態，此外，亦可平均熱交換元件內的壓力。 2. The heat exchange element provided by the present invention is particularly provided with a plurality of second longitudinal cooling fluid channels at a position below the vapor zone, and the distance between the channels is shortened due to an increase in the number, so that the cooling fluid can be balanced in The water level between each of the second longitudinal cooling fluid channels avoids a situation where the water level in a specific position is too low and causes a high temperature in a local position. In addition, the pressure in the heat exchange element can be averaged.
本發明已透過上述之實施例揭露如上，然其並非用以限定本發明，任何熟悉此一技術領域具有通常知識者，在瞭解本發明前述的技術特徵及實施例，並在不脫離本發明之精神和範圍內，不可作些許之更動與潤飾，因此本發明之專利保護範圍須視本說明書所附之請求項所界定者為準。 The present invention has been disclosed as above through the above-mentioned embodiments, but it is not intended to limit the present invention. Anyone with ordinary knowledge in this technical field will understand the aforementioned technical features and embodiments of the present invention without departing from the scope of the present invention. Within the spirit and scope, minor changes and retouching are not allowed. Therefore, the scope of patent protection of the present invention shall be subject to the definition in the claims attached to this specification.
Claims (6)
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| TW107133405A TWI663371B (en) | 2018-09-21 | 2018-09-21 | Evaporator structure |
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| TW107133405A TWI663371B (en) | 2018-09-21 | 2018-09-21 | Evaporator structure |
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| US20040211551A1 (en) * | 2001-11-15 | 2004-10-28 | Etsuo Shinmura | Heat exchanger, heat exchanger header tank and manufacturing method thereof |
| CN101672553A (en) * | 2009-09-25 | 2010-03-17 | 华南理工大学 | Parallel stream heat exchanger integrated with microchannel and outer fin |
| CN101701756A (en) * | 2009-10-22 | 2010-05-05 | 天津三电汽车空调有限公司 | Parallel flow evaporator and flow clapboard thereof |
| US20130014915A1 (en) * | 2011-07-13 | 2013-01-17 | Stefan Hirsch | Accumulator for a cooling fluid and heat exchanger |
| TW201719100A (en) * | 2015-11-20 | 2017-06-01 | Kuettner Asia Company Ltd | Heat exchanger capable of preventing high temperature gas in the high temperature passageway from being leaked to the low temperature passageway |
| TW201743028A (en) * | 2016-04-18 | 2017-12-16 | Ｑｃｉｐ控股有限責任公司 | Microchannel evaporators with reduced pressure drop |
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|---|---|---|---|---|
| US20040211551A1 (en) * | 2001-11-15 | 2004-10-28 | Etsuo Shinmura | Heat exchanger, heat exchanger header tank and manufacturing method thereof |
| CN101672553A (en) * | 2009-09-25 | 2010-03-17 | 华南理工大学 | Parallel stream heat exchanger integrated with microchannel and outer fin |
| CN101701756A (en) * | 2009-10-22 | 2010-05-05 | 天津三电汽车空调有限公司 | Parallel flow evaporator and flow clapboard thereof |
| US20130014915A1 (en) * | 2011-07-13 | 2013-01-17 | Stefan Hirsch | Accumulator for a cooling fluid and heat exchanger |
| TW201719100A (en) * | 2015-11-20 | 2017-06-01 | Kuettner Asia Company Ltd | Heat exchanger capable of preventing high temperature gas in the high temperature passageway from being leaked to the low temperature passageway |
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