TW201036527A - Large-area liquid-cooled heat-dissipation device - Google Patents
Large-area liquid-cooled heat-dissipation device Download PDFInfo
- Publication number
- TW201036527A TW201036527A TW098108854A TW98108854A TW201036527A TW 201036527 A TW201036527 A TW 201036527A TW 098108854 A TW098108854 A TW 098108854A TW 98108854 A TW98108854 A TW 98108854A TW 201036527 A TW201036527 A TW 201036527A
- Authority
- TW
- Taiwan
- Prior art keywords
- heat
- liquid
- tubes
- absorbing
- distributor
- Prior art date
Links
Classifications
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
- H01L23/00—Details of semiconductor or other solid state devices
- H01L23/34—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements
- H01L23/46—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids
- H01L23/473—Arrangements for cooling, heating, ventilating or temperature compensation ; Temperature sensing arrangements involving the transfer of heat by flowing fluids by flowing liquids
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28D—HEAT-EXCHANGE APPARATUS, NOT PROVIDED FOR IN ANOTHER SUBCLASS, IN WHICH THE HEAT-EXCHANGE MEDIA DO NOT COME INTO DIRECT CONTACT
- F28D15/00—Heat-exchange apparatus with the intermediate heat-transfer medium in closed tubes passing into or through the conduit walls ; Heat-exchange apparatus employing intermediate heat-transfer medium or bodies
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F1/00—Tubular elements; Assemblies of tubular elements
- F28F1/10—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses
- F28F1/12—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element
- F28F1/14—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally
- F28F1/22—Tubular elements and assemblies thereof with means for increasing heat-transfer area, e.g. with fins, with projections, with recesses the means being only outside the tubular element and extending longitudinally the means having portions engaging further tubular elements
-
- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F28—HEAT EXCHANGE IN GENERAL
- F28F—DETAILS OF HEAT-EXCHANGE AND HEAT-TRANSFER APPARATUS, OF GENERAL APPLICATION
- F28F3/00—Plate-like or laminated elements; Assemblies of plate-like or laminated elements
- F28F3/12—Elements constructed in the shape of a hollow panel, e.g. with channels
-
- H—ELECTRICITY
- H01—ELECTRIC ELEMENTS
- H01L—SEMICONDUCTOR DEVICES NOT COVERED BY CLASS H10
- H01L2924/00—Indexing scheme for arrangements or methods for connecting or disconnecting semiconductor or solid-state bodies as covered by H01L24/00
- H01L2924/0001—Technical content checked by a classifier
- H01L2924/0002—Not covered by any one of groups H01L24/00, H01L24/00 and H01L2224/00
Abstract
Description
201036527 六、發明說明: 【發明所屬之技術領域】 本發明係關於一種大面積液冷式散熱裝置,尤指一種 具針對不同位置之散熱需求而提供不同散熱效果的大面積 - 液冷式散熱裝置。 % * 【先前技術】 目前一般電腦,例如個人電腦、伺服器等,其所要處 Ο 理的運算工作日益繁雜,故晶片及半導體開關等多個電子 元件工作時所產生的廢熱溫度極高,為使該些電子元件降 溫,通常係於電子元件上加裝一風扇或液冷散熱裝置,以 對電子元件進行散熱。 為有效地令多個發熱電子元件散熱,請參閱第十一圖 所示,一種既有應用於伺服器之大面積液冷式散熱裝置包 括一熱擴散板(60)及一具有單一管徑的吸熱管(7〇),其中該 熱擴散板(60)係具有一供與伺服器之電子元件(8〇)直接接 〇 觸的吸熱面(61)及一散熱面(62),而該吸熱管(70)係蜿蜒地 設於該熱擴散板(60)之散熱面(62)上,以平均分布於該熱擴 散板(60)之散熱面(62)上而構成熱接觸,又該吸熱管(7〇)具 有一入口端(71)及一出口端(72),該入口端(71)係供將冷卻 液注入該吸熱管(70)中,藉由冷卻液流經吸熱管(7〇)時,一 併對熱擴散板(60)自電子元件(8〇)吸取的廢熱進行熱交 換,以將堆積於熱擴散板(6〇)上的廢熱帶走,進而達到對電 子元件(80)散熱降溫的效果。 惟上述大面積液冷式散熱裝置具有以下缺點: 3 201036527 1·為令該單一吸熱管(70)可平均分布於該熱擴散板(6〇) 上’以對該熱擴散板(60)之散熱面(62)上各處吸熱,勢必要 設計令該單一吸熱管(7〇)具有多處彎折,方得使該單一吸熱 管(70)藉由蜿蜒地來回延伸,而平均地分布設置於該熱擴散 板(60)上,然而過多的彎折,將造成冷卻液於吸熱管中 傳遞的阻礙,導致該大面積液冷式散熱裝置必須使用較強 力的泵方可令冷卻液順暢地於該吸熱管(7〇)中流動。 Ο Ο 2_為令該單一吸熱管(70)可平均分布於該大面積液冷 式散熱裝置之熱擴散板(60)上,該單一吸熱管(7〇)的長度必 須夠長,方可將該單一吸熱管(70)以多處彎折的設計,蜿蜒 =刀布設置於該熱擴散板(6Q)上,然婉蜒設置必然造成吸熱 管(7〇)的長度較長,如此將造成流經入口端(71)及出口端 (72)的冷卻液之間具有過大的溫差,導致該吸熱管(7〇)上靠 近該單-吸熱管(70)出口端(72)處的熱交換能力與靠近該 單-吸熱管(70)出口端(72)處的熱交換能力有明顯的差 異因此’伺服器主機板在設計時,亦必須針對該大面積 =冷式散熱裝置散熱能力不均的缺點,而調整祠服器主機 :上電子元件(80)的線路佈局,例如發熱溫度較高的電子元 =〇):須設計在對應靠近吸熱管(7〇)入口端處因而 长向了線路佈局的複雜度。 問201036527 VI. Description of the Invention: [Technical Field] The present invention relates to a large-area liquid-cooled heat sink, and more particularly to a large-area-liquid-cooled heat sink having different heat dissipation effects for different positions of heat dissipation . % * [Prior Art] At present, general computer, such as personal computers, servers, etc., are increasingly complicated in computing operations, so the waste heat generated by the operation of multiple electronic components such as chips and semiconductor switches is extremely high. To cool the electronic components, a fan or a liquid cooling heat sink is usually attached to the electronic components to dissipate heat from the electronic components. In order to effectively dissipate heat from a plurality of heat-generating electronic components, as shown in FIG. 11 , a large-area liquid-cooled heat sink device for use in a server includes a heat diffusion plate (60) and a single pipe diameter. a heat absorbing tube (7), wherein the heat diffusion plate (60) has a heat absorbing surface (61) for directly contacting the electronic component (8 〇) of the server and a heat dissipating surface (62), and the heat absorbing surface The tube (70) is disposed on the heat dissipating surface (62) of the heat diffusion plate (60), and is evenly distributed on the heat dissipating surface (62) of the heat diffusion plate (60) to form a thermal contact. The heat absorbing tube (7 〇) has an inlet end (71) and an outlet end (72) for injecting a cooling liquid into the heat absorbing tube (70) through the cooling liquid flowing through the heat absorbing tube ( 7〇), heat exchange of the waste heat absorbed by the heat diffusion plate (60) from the electronic component (8〇) to remove the waste tropical water accumulated on the heat diffusion plate (6〇), thereby achieving the electronic component (80) The effect of cooling and cooling. However, the above-mentioned large-area liquid-cooled heat sink has the following disadvantages: 3 201036527 1 · The single heat absorbing tube (70) can be evenly distributed on the heat diffusion plate (6 〇) to the heat diffusion plate (60) The heat dissipation surface (62) absorbs heat everywhere, and it is necessary to design the single heat absorbing tube (7 〇) to have multiple bends, so that the single heat absorbing tube (70) is evenly distributed by squatting back and forth. Provided on the heat diffusion plate (60), however, too much bending will cause the coolant to pass through the heat absorbing tube, resulting in the large area liquid cooling heat sink must use a stronger pump to make the coolant smooth The ground flows in the heat absorbing tube (7 〇). Ο Ο 2_ is such that the single heat absorbing tube (70) can be evenly distributed on the heat diffusion plate (60) of the large-area liquid-cooled heat sink, and the length of the single heat absorbing tube (7 〇) must be long enough. The single heat absorbing tube (70) is designed to be bent at a plurality of places, and the 蜿蜒=knife cloth is disposed on the heat diffusion plate (6Q), and then the setting of the heat absorbing tube (7 〇) is inevitably caused to be long. An excessive temperature difference between the coolant flowing through the inlet end (71) and the outlet end (72) is caused to cause the heat absorbing tube (7 〇) to be adjacent to the outlet end (72) of the single-heat absorbing tube (70). The heat exchange capability is significantly different from the heat exchange capability near the outlet end (72) of the single-heat absorption tube (70). Therefore, the 'server board must also be designed for the large area = cooling capacity of the cooling device. The disadvantage of unevenness, and adjust the servo host: the circuit layout of the upper electronic component (80), such as the electronic element with higher heating temperature = 〇): must be designed to be close to the entrance end of the heat absorbing tube (7 〇) and thus long Towards the complexity of the line layout. ask
【發明内容】 為解決既有大面積 題,本發明之主要目 ’其可針對不同位置 液冷式散熱裝置之散熱效果不均的 的在提供一種大面積液冷式散熱裝 之散熱需求而提供不同散熱效果。 4 201036527 為達成前述目的所採取之主要技術手段係令前述液冷 式散熱裝置包括: 一熱擴散板’係具有一吸熱面及一散熱面,其中該吸 熱面係供與多個發熱源接觸; ' 一注液分布器,係具有至少一入水口及複數送水口; 複數吸熱管’係分布設於該熱擴散板之散熱面上,且 各吸熱管係具有一入口端及一出口端,其中該複數吸熱管 的入口端係分別與該注液分布器的複數送水口連接,而與 〇 該注液分布器連通,又各吸熱管内係具有一冷卻液通道, 且該複數吸熱管之冷卻液通道的截面積均不相同,具有較 大冷卻液通道截面積之吸熱管係對應溫度較高的發熱源; 一排液收集器’具有至少一出水口及複數進水口,其中該 複數進水口係分別與該複數吸熱管的出口端連接,並透過 該複數吸熱管與該注液分布器連通。 利用上述技術手段,由於本液冷式散熱裝置使用較多 的吸熱管’故各吸熱管可設計以最少的彎管次數,分布設 Ο 於該熱擴散板上,藉此減少冷卻液於吸熱管中傳遞時的祖 礙;此外’再將具有較大截面積冷卻液通道之吸熱管與溫 度較高的發熱源對應設置,可提高對溫度較高發熱源之吸 熱效果,故可由本散熱裝置配合線路佈局,在設計上較有 彈性’並可減少線路佈局的負擔。 【實施方式】 關於本發明之第一實施例,請參閱第一至四圖所示, 係包括一熱擴散板(10)、一注液分布器(20)、複數吸熱管(30) 5 201036527 及一排液收集器(40)。 上述熱擴散板(10)係具有一吸熱面(11)及一散熱面 (12) ’其中該吸熱面(1彳)係供與多個發熱源(5〇)構成熱接 觸’例如伺服器主機板上的電子元件;於本實施例中,該 熱擴散板(10)係為一矩形片狀板體。 請進一步參閱第四圖所示,上述注液分布器(20)係具有 至少一入水口(21)及複數送水口(22);於本實施例中,該注 液分布器(20)係焊接設於該熱擴散板(1〇)之散熱面(彳2)上, 〇 並鄰近該矩形片狀熱擴散板(10)之其中一侧邊,又該注液分 布器(20)係為一中空矩形立方體,其具有一頂壁、一底壁及 複數側壁,其中該頂壁和底壁係相對設置,而該複數側壁 則與該頂壁及底壁垂直地鄰接,又該入水口(2彳)係設於其中 一側壁上,而該送水口(22)係設於其他的側壁上。 上述吸熱管(30)係分布設於該熱擴散板(1〇)之散熱面 (12)上,又各吸熱管(3〇)係具有一入口端(31)及一出口端 (32),其中該複數吸熱管(30)的入口端(31)係分別與該注液 〇 分布器(20)的複數送水口(22)連接,而與該注液分布器(2〇) 連通,又各吸熱管(30)内具有一冷卻液通道,且各吸熱管(3〇) 之冷卻液通道分屬至少兩種不同的截面積,該冷卻液通道 的截面積種類可等於或不等於吸熱管(3〇)的數量,例如: 熱管(30)為兩支時’其冷卻液通道分別為兩種不同的戴面 積’二支吸熱管(30)時,其冷卻液通道可以分屬兩種咬二種 不同的截面積,四支吸熱管(30)時則其冷卻液通道可分別為 二至四種不同的截面積,並可依此類推;其中:具有較大 冷卻液通道截面積之吸熱管(30)係對應溫度較高的發熱原 6 201036527 (50),於本實&例中,該複數吸熱管州係呈環狀迴路且 焊設於該熱擴散板(1。)之散熱面(12)上,且較長的吸熱管 (30)具有較寬的官後’而以吸熱管(3q)管徑的寬窄決定吸熱 管(3〇)之冷卻液通道的截面積大小,又該複數吸熱管(30)i 有不同的長度’且本實施例中該吸熱管(3G)之長度與其内部 冷卻液《的截面積大小成正比,即較長吸熱管⑽)之冷卻 液通道的截面積較大’目而具有較大的冷卻液流量,故具 Ο 有較佳的吸熱效果’將之與溫度較高的發熱源(5〇)對應設置 可充分地對溫度較高的發熱源(5Q)散熱,而冷卻液通道的截 面積較小之吸熱管(30)則因冷卻液流量較小,故與溫度較低 的發熱源(50)對應設置。 上述排液收集器(4 0)係具有至少一出水口( 4彳)及複數 進水口(42),其中該複數進水口(42)係分別與該複數吸熱管 (30)的出口端(32)連接,而透過該複數吸熱管(3〇)與該注液 分布器(20)連通,於本實施例中,該排液收集器(4〇)係焊接 設於該熱擴散板(10)之散熱面(12)上,並與該注液分布器 Ο (20)設於該矩形片狀熱擴散板(1〇)之同一側邊,又該排液收 集器(40)係為一中空矩形立方體,其具有一頂壁一底壁及 複數側壁,其中該頂壁和底壁係相對設置,而該複數側壁 則與該頂壁及底壁垂直地鄰接,又該出水口(41)係設於其中 一側壁上,而該進水口( 4 2)係設於其他的側壁上。 另關於本發明之第二實施例,請參閱第五圖所示,其 與第一實施例大致相同,不同之處在於:該熱擴散板(彳〇) 係包括一下蓋板(101)及一上蓋板(102),其中: 該下蓋板(1 01)的之底面係該熱擴散板(1 〇)的吸熱面 7 201036527 (11) ,而該下蓋板(101)之頂面上係於對應該第一實施例中 之注液分布器(20)、吸熱管(30)及排液收集器(40)的設置位 置處,形成有一下注液分布器欲槽(1〇1a)、複數下吸熱管傲 槽(101b)及一下排液收集器嵌槽(101c); 該上蓋板(102)之頂面係該熱擴散板(1〇)的散熱面 (12) ,而該上蓋板(102)之底面則形成有一上注液分布器嵌 槽(102a)、複數上吸熱管嵌槽(102 b)及一上排液收集器嵌槽 (102c),其中該上注液分布器嵌槽(102a)、上吸熱管嵌槽 〇 (102b)及上排液收集器嵌槽(102C)係對應該下蓋板(1〇1)的 下注液分布器嵌槽(101 a)、下吸熱管嵌槽(101b)及下排液收 集器嵌槽(101c),藉由將上蓋板(102)以其底面蓋設於該下 蓋板(101)的頂面上,而由上、下注液分布器嵌槽 (1〇2a)(1〇la)、上' 下吸熱管嵌槽(102b)(101b)及上、下排 液收集器嵌槽(102c)(101c)構成第一實施例中的注液分布 器(2〇)、吸熱管(30)及排液收集器(40),藉由調整上、下吸 熱管嵌槽(102b)(101b)的深度,即可改變吸熱管中冷卻液通 Ο 道的截面積,故亦可隨需求讓冷卻液通道截面積較大的下 吸熱管嵌槽(1〇1b)對應溫度較高的發熱源(50)處。 又關於本發明之第三實施例,請進一步參閱第六圖所 示’其與第一實施例大致相同,不同之處在於:本第三實 施例並非以吸熱管(30)管徑的寬窄決定吸熱管(30)之冷卻 液通道的截面積大小,而是以不同的管内壁設計達成,於 本實施例中,係使用四條吸熱管(30),其中: 請參閱第七圖所示,最長吸熱管(30)内係具有一平滑内 壁(301); 8 201036527 明參閱第八圖所示,次長吸熱管(30)内係具有一鋸齒内 壁(302广 請參閱第九圖所示’次短吸熱管(30)内係具有一粗糙内 壁(303); 清參閱第十圖所示,最短吸熱管(30)内係設有複數柵網 (304); 如此’亦可讓吸熱管(30)的冷卻液通道截面積大小不 同。 〇 是以’本液冷式散熱裝置具有以下優點: 1·由於本液冷式散熱裝置係使用複數吸熱管(3〇),由該 複數吸熱管(30)共同地分布設於該熱擴散板(1 〇)上,因此可 將每個吸熱管(30)的彎管次數減至最少,如此一來,即可減 少冷卻液於吸熱管(30)中傳遞所造成的壓損,故毋須使用較 強力的泵即可令冷卻液順暢地於該吸熱管(3〇)中流動。 2_由於冷卻液通道截面積較大的吸熱管(30)可讓較多 的冷卻液流過,故根據熱量計算公式g = p么:熱量對 〇 時間微分’ C/>:隨溫度變化的流體比熱;f :流量;p:流 體密度;vr:溫度變化量),冷卻液通道截面積較大的吸熱 管(30)因其内冷卻液流量較大,故其整體吸熱能力較強,適 合用以對溫度較高的發熱源(5〇)進行散熱。 3.雖較長之吸熱管(30)的入口端(31)及出口端(32)處的 冷卻液溫差較大,導致較長之吸熱管(3〇)的出口端(32)處吸 熱效果較差,然由於較長吸熱管(30)之冷卻液通道的载面積 較大’因此可使較多的冷卻液流過,故根據前述熱量計算 公式,較長吸熱管(30)因其内冷卻液流量較大而得於出口端 9 201036527 (32)處維持足夠的吸熱效果。因此,可將各吸熱管⑴從入 口端(31)至出口端(32)的吸熱效果差異減至最小,故本液冷 式散熱裝置可提供穩定且平均的散熱效果。 惟本發明雖已於前述實施例中所揭露,但並不僅限於 刖述實施例中所提及之内容,在不脫離本發明之精神和範 圍内所作之任何變化與修改,均屬於本發明之保護範圍。 综上所述’本發明已具備顯著功效增進,並符合發明 專利要件’爰依法提起申請。SUMMARY OF THE INVENTION In order to solve the problem of large-area liquid-cooled heat sinks, the main purpose of the present invention is to provide a large-area liquid-cooled heat sink with different heat dissipation effects for different positions of the liquid-cooled heat sink. Different heat dissipation effects. 4 201036527 The main technical means for achieving the foregoing objective is that the liquid-cooled heat sink comprises: a heat diffusion plate having a heat absorbing surface and a heat dissipating surface, wherein the heat absorbing surface is in contact with a plurality of heat sources; An infusion distributor has at least one water inlet and a plurality of water supply ports; a plurality of heat absorption tubes are distributed on the heat dissipation surface of the heat diffusion plate, and each of the heat absorption tubes has an inlet end and an outlet end, wherein The inlet ends of the plurality of heat absorption tubes are respectively connected to the plurality of water supply ports of the liquid injection distributor, and are connected to the liquid injection distributor, and each of the heat absorption tubes has a coolant passage, and the coolant of the plurality of heat absorption tubes The cross-sectional area of the channel is different, and the heat-absorbing tube having a larger cross-sectional area of the coolant channel corresponds to a heat source having a higher temperature; the liquid-collecting device has at least one water outlet and a plurality of water inlets, wherein the plurality of water inlets Connected to the outlet end of the plurality of heat absorption tubes, respectively, and communicated with the liquid injection distributor through the plurality of heat absorption tubes. By using the above technical means, since the liquid cooling type heat sink uses a large number of heat absorbing tubes, each heat absorbing tube can be designed with a minimum number of bends, and is distributed on the heat diffusion plate, thereby reducing the coolant in the heat absorbing tube. In addition, the heat transfer tube with a larger cross-sectional area coolant channel is arranged correspondingly to the heat source with higher temperature, which can improve the heat absorption effect of the heat source with higher temperature, so the heat sink can be used with the line. The layout is more flexible in design and can reduce the burden of the line layout. [Embodiment] With regard to the first embodiment of the present invention, please refer to the first to fourth figures, including a heat diffusion plate (10), a liquid injection distributor (20), and a plurality of heat absorption tubes (30) 5 201036527 And a drain collector (40). The heat diffusion plate (10) has a heat absorbing surface (11) and a heat dissipating surface (12). The heat absorbing surface (1) is configured to be in thermal contact with a plurality of heat sources (5 〇), such as a server host. The electronic component on the board; in the embodiment, the heat diffusion plate (10) is a rectangular sheet-like plate body. Further, as shown in the fourth figure, the liquid-injecting distributor (20) has at least one water inlet (21) and a plurality of water supply ports (22); in the embodiment, the liquid-injecting distributor (20) is welded. It is disposed on a heat dissipating surface (彳2) of the heat diffusion plate (1〇), adjacent to one side of the rectangular sheet-shaped heat diffusion plate (10), and the liquid-injecting distributor (20) is a a hollow rectangular cube having a top wall, a bottom wall and a plurality of side walls, wherein the top wall and the bottom wall are oppositely disposed, and the plurality of side walls are vertically adjacent to the top wall and the bottom wall, and the water inlet (2)彳) is provided on one of the side walls, and the water supply port (22) is provided on the other side wall. The heat absorbing tube (30) is disposed on the heat dissipating surface (12) of the heat diffusion plate (1), and each of the heat absorbing tubes (3) has an inlet end (31) and an outlet end (32). The inlet end (31) of the plurality of heat absorption tubes (30) is respectively connected to the plurality of water supply ports (22) of the liquid injection distributor (20), and is connected to the liquid injection distributor (2〇), and each The heat absorbing tube (30) has a coolant passage therein, and the coolant passages of the heat absorbing tubes (3 〇) belong to at least two different cross-sectional areas, and the cross-sectional area of the coolant passages may be equal to or not equal to the heat absorbing tubes ( The number of 3〇), for example: when the heat pipe (30) is two, when the coolant passages are two different wearing areas, respectively, the two heat absorption pipes (30), the coolant passages can be divided into two kinds of bites. Different cross-sectional areas, four heat-absorbing tubes (30), the coolant channels can be two to four different cross-sectional areas, and so on; wherein: the heat pipe with a larger coolant channel cross-sectional area (30) corresponds to a relatively high temperature pyrogen 6 201036527 (50), in the present & example, the plural heat pipe state The annular circuit is soldered to the heat dissipating surface (12) of the heat diffusion plate (1), and the longer heat absorbing tube (30) has a wider width of the front and the width of the tube of the heat absorbing tube (3q) Determining the cross-sectional area of the coolant passage of the heat absorbing tube (3 〇), and the plurality of heat absorbing tubes (30) i have different lengths 'and the length of the heat absorbing tube (3G) and the internal coolant thereof in this embodiment The area is proportional to the size, that is, the longer the cross-sectional area of the coolant channel of the longer heat absorbing tube (10) is larger, and has a larger coolant flow rate, so it has a better heat absorption effect. The source (5 〇) correspondingly can dissipate heat to the heat source (5Q) with a higher temperature, and the heat absorbing tube (30) with a smaller cross-sectional area of the coolant channel has a lower flow rate of the coolant, so the temperature is lower. The heat source (50) corresponds to the setting. The liquid discharge collector (40) has at least one water outlet (4 彳) and a plurality of water inlets (42), wherein the plurality of water inlets (42) are respectively connected with the outlet ends of the plurality of heat absorbing tubes (30) (32) Connected to the liquid-injecting distributor (20) through the plurality of heat-absorbing tubes (3〇). In the present embodiment, the liquid-collecting collector (4〇) is welded to the heat-diffusing sheet (10) The heat dissipating surface (12) is disposed on the same side of the rectangular sheet-shaped heat diffusion plate (1) as the liquid-distributing distributor 20 (20), and the liquid-discharging collector (40) is hollow. a rectangular cube having a top wall, a bottom wall and a plurality of side walls, wherein the top wall and the bottom wall are oppositely disposed, and the plurality of side walls are vertically adjacent to the top wall and the bottom wall, and the water outlet (41) is It is disposed on one of the side walls, and the water inlet (42) is disposed on the other side wall. Referring to the second embodiment of the present invention, please refer to the fifth embodiment, which is substantially the same as the first embodiment, except that the heat diffusion plate (彳〇) includes a lower cover plate (101) and a An upper cover plate (102), wherein: a bottom surface of the lower cover plate (1 01) is a heat absorption surface 7 201036527 (11) of the heat diffusion plate (1 ,), and a top surface of the lower cover plate (101) A placement of a liquid injection distributor (1〇1a) is formed at a position corresponding to the liquid injection distributor (20), the heat absorption tube (30), and the liquid discharge collector (40) in the first embodiment. a plurality of heat absorbing tubes (101b) and a lower drain collector slot (101c); the top surface of the upper cover (102) is a heat dissipating surface (12) of the heat diffusion plate (1), and the The bottom surface of the upper cover plate (102) is formed with an upper liquid distributor distributor groove (102a), a plurality of upper heat absorption tube insertion grooves (102b) and an upper liquid collection collector insertion groove (102c), wherein the liquid injection liquid The distributor slot (102a), the upper heat pipe slot (102b) and the upper drain collector slot (102C) are corresponding to the lower cover (1〇1) of the lower liquid distributor slot (101a) ), under the heat The tube insertion groove (101b) and the lower liquid collection collector groove (101c) are provided by the upper cover plate (102) being covered on the top surface of the lower cover plate (101) by the bottom surface thereof The first embodiment of the injection distributor slot (1〇2a) (1〇la), the upper 'lower heat pipe recess (102b) (101b) and the upper and lower drain collector slots (102c) (101c) constitute the first implementation In the example, the liquid injection distributor (2〇), the heat absorption tube (30) and the liquid discharge collector (40) can change the heat absorption tube by adjusting the depths of the upper and lower heat absorption tube fitting grooves (102b) (101b). The cross-sectional area of the middle coolant passage channel, so that the lower heat-absorbing tube insert groove (1〇1b) having a larger cross-sectional area of the coolant passage can be corresponding to the heat source (50) having a higher temperature. With regard to the third embodiment of the present invention, please refer to the sixth embodiment, which is substantially the same as the first embodiment, except that the third embodiment is not determined by the width of the heat pipe (30). The cross-sectional area of the coolant passage of the heat absorbing tube (30) is achieved by different inner wall design. In this embodiment, four heat absorbing tubes (30) are used, wherein: Please refer to the seventh figure, the longest The heat absorbing tube (30) has a smooth inner wall (301); 8 201036527 As shown in the eighth figure, the second long heat absorbing tube (30) has a sawtooth inner wall (302 is wide as shown in the ninth figure) The heat absorbing tube (30) has a rough inner wall (303); as shown in the tenth figure, the shortest heat absorbing tube (30) is provided with a plurality of grids (304); thus 'allowing the heat absorbing tube (30) The cross-sectional area of the coolant channel is different. 〇 The liquid cooling device has the following advantages: 1. Since the liquid cooling device uses a plurality of heat absorbing tubes (3 〇), the plurality of heat absorbing tubes (30) Co-distributed on the heat diffusion plate (1 〇), so Minimize the number of bends per heat pipe (30), thus reducing the pressure loss caused by the transfer of coolant in the heat absorbing tube (30), so it is not necessary to use a stronger pump to cool The liquid flows smoothly in the heat absorbing tube (3〇). 2_ Since the heat absorbing tube (30) having a large cross-sectional area of the coolant passage allows more coolant to flow, the formula g = p is calculated according to the heat: Heat vs. time differential 'C/>: specific heat of fluid as a function of temperature; f: flow rate; p: fluid density; vr: temperature change amount), the heat absorbing tube (30) having a larger cross-sectional area of the coolant passage is inside The coolant flow rate is large, so its overall heat absorption capacity is strong, which is suitable for heat dissipation of a relatively high temperature heat source (5 〇). 3. Although the temperature difference of the coolant at the inlet end (31) and the outlet end (32) of the longer heat absorbing tube (30) is large, the heat absorption effect at the outlet end (32) of the longer heat absorbing tube (3 〇) is caused. Poor, because the coolant channel of the longer heat absorbing tube (30) has a larger carrying area, so more coolant can flow through, so the longer heat absorbing tube (30) is cooled by the heat according to the aforementioned heat calculation formula. The liquid flow rate is large and sufficient endothermic effect is maintained at the outlet end 9 201036527 (32). Therefore, the difference in heat absorption effect of each heat absorbing tube (1) from the inlet end (31) to the outlet end (32) can be minimized, so that the liquid cooling heat sink can provide a stable and average heat dissipation effect. However, the present invention has been disclosed in the foregoing embodiments, but is not limited to the details of the embodiments, and any changes and modifications made without departing from the spirit and scope of the invention belong to the present invention. protected range. In summary, the present invention has been provided with significant improvement in efficacy and in accordance with the invention patent requirements.
D 【圖式簡單說明】 第一圖:係本發明第一實施例之外觀圖。 第一圖.係本發明第一實施例之部分分解圖。 第三圖··係本發明第一實施例之分解圖。 第四圖:係本發明第一實施例之俯視圖。 第五圖:係本發明第二實施例之分解圖。 第六圖:係本發明第三實施例之外觀圖。 帛ϋ本發明第三實施例中最長吸熱管之剖面圖。 第八圖:係本發明第三實施例中次長吸熱管之剖面圖。 第九圖:係本發明第三實施例中次短吸熱管之剖面圖。 第十圖:係本發明第三實施例中最短吸熱管之剖面圖。 第十-圖:係、既有Α面積液冷式散熱裝置的外觀圖。 【主要元件符號說明】 (1〇1a)下注液分布器嵌槽 (1〇)熱擴散板 (101)下蓋板 201036527 (101b)下吸熱管嵌槽 (101c)下排液收集器嵌槽 (102)上蓋板 (102a)上注液分布器嵌槽 (102b)上吸熱管嵌槽 (102c)上排液收集器嵌槽 (11)吸熱面 (12)散熱面 (20)注液分布器 (21)入水口 (22)送水口 (30)吸熱管 (301)平滑内壁 (302)鋸齒内壁 (303)—粗糙内壁 (304)栅網 (31)入口端 (32)出口端 (40)排液收集器 (41)出水口 (42)進水口 (50)發熱源 (60)熱擴散板 (61)吸熱面 (62)散熱面 (70)吸熱管 (71)入口端 (72)出口端 (80)電子元件 Ο 11D [Simplified Description of the Drawings] The first drawing is an external view of the first embodiment of the present invention. The first figure is a partially exploded view of a first embodiment of the present invention. Fig. 3 is an exploded view of the first embodiment of the present invention. Fourth Figure: is a plan view of a first embodiment of the present invention. Figure 5 is an exploded view of a second embodiment of the present invention. Figure 6 is an external view of a third embodiment of the present invention. A cross-sectional view of the longest heat absorbing tube in the third embodiment of the present invention. Figure 8 is a cross-sectional view showing a secondary long heat absorbing tube in a third embodiment of the present invention. Figure 9 is a cross-sectional view showing a secondary short heat absorbing tube in a third embodiment of the present invention. Figure 10 is a cross-sectional view showing the shortest heat absorbing tube in the third embodiment of the present invention. Tenth-figure: The appearance of a liquid-cooled heat sink with a Α area. [Main component symbol description] (1〇1a) Underfill distributor spreader (1〇) Thermal diffusion plate (101) Lower cover 201036527 (101b) Lower heat pipe groove (101c) Lower drain collector groove (102) Upper cover plate (102a) on the liquid distribution distributor groove (102b) on the heat absorption pipe groove (102c) on the liquid collector collector groove (11) heat absorption surface (12) heat dissipation surface (20) injection liquid distribution (21) water inlet (22) water supply port (30) heat absorption tube (301) smooth inner wall (302) serrated inner wall (303) - rough inner wall (304) grid (31) inlet end (32) outlet end (40) Drain collector (41) water outlet (42) water inlet (50) heat source (60) heat diffusion plate (61) heat absorption surface (62) heat dissipation surface (70) heat absorption tube (71) inlet end (72) outlet end (80) Electronic components Ο 11
Claims (1)
Priority Applications (2)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
TW098108854A TW201036527A (en) | 2009-03-19 | 2009-03-19 | Large-area liquid-cooled heat-dissipation device |
US12/586,324 US20100236761A1 (en) | 2009-03-19 | 2009-09-21 | Liquid cooled heat sink for multiple separated heat generating devices |
Applications Claiming Priority (1)
Application Number | Priority Date | Filing Date | Title |
---|---|---|---|
TW098108854A TW201036527A (en) | 2009-03-19 | 2009-03-19 | Large-area liquid-cooled heat-dissipation device |
Publications (2)
Publication Number | Publication Date |
---|---|
TW201036527A true TW201036527A (en) | 2010-10-01 |
TWI372596B TWI372596B (en) | 2012-09-11 |
Family
ID=42736480
Family Applications (1)
Application Number | Title | Priority Date | Filing Date |
---|---|---|---|
TW098108854A TW201036527A (en) | 2009-03-19 | 2009-03-19 | Large-area liquid-cooled heat-dissipation device |
Country Status (2)
Country | Link |
---|---|
US (1) | US20100236761A1 (en) |
TW (1) | TW201036527A (en) |
Families Citing this family (5)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
WO2010037872A1 (en) * | 2008-10-02 | 2010-04-08 | Ibérica Del Espacio, S.A. | Spaceship heat module |
CN201449171U (en) * | 2009-05-05 | 2010-05-05 | 蔡应麟 | Tubular energy saver |
CN102791113A (en) * | 2012-08-16 | 2012-11-21 | 广州高澜节能技术股份有限公司 | Cooling pipeline system in multi-megawatt converter cabinet |
DE102013212724B3 (en) | 2013-06-28 | 2014-12-04 | TRUMPF Hüttinger GmbH + Co. KG | Cooling device for cooling an electronic component and electronic assembly with a cooling device |
TWI624640B (en) * | 2017-01-25 | 2018-05-21 | 雙鴻科技股份有限公司 | Liquid-cooling heat dissipation device |
Family Cites Families (126)
Publication number | Priority date | Publication date | Assignee | Title |
---|---|---|---|---|
US2064141A (en) * | 1934-03-16 | 1936-12-15 | Fedders Mfg Co Inc | Method of making refrigerating apparatus |
US2271648A (en) * | 1937-05-28 | 1942-02-03 | Dole Refrigerating Co | Liquid cooling device |
US2436389A (en) * | 1945-09-04 | 1948-02-24 | Dole Refrigerating Co | Refrigerating plate and internal reinforcement therefor |
US2487674A (en) * | 1947-03-06 | 1949-11-08 | Richard A Rott | Cabinet defrosting device |
US2538014A (en) * | 1947-05-05 | 1951-01-16 | Dole Refrigerating Co | Freezer plate |
US2638754A (en) * | 1949-03-02 | 1953-05-19 | Dole Refrigerating Co | Refrigerant plate |
US2737027A (en) * | 1950-11-04 | 1956-03-06 | Air conditioning structure | |
US2734344A (en) * | 1953-05-01 | 1956-02-14 | lindenblad | |
US2910094A (en) * | 1956-05-31 | 1959-10-27 | Foil Process Corp | Tube-providing sheet |
US3011323A (en) * | 1957-10-23 | 1961-12-05 | Carbonic Dispenser Inc | Ice plate |
US3001382A (en) * | 1958-06-16 | 1961-09-26 | Reflectotherm Inc | Radiant cooling systems |
FR1313251A (en) * | 1961-11-15 | 1962-12-28 | Tube forging process by fast reciprocating machine | |
US3269459A (en) * | 1963-03-12 | 1966-08-30 | Popovitch Dragolyoub | Extensive surface heat exchanger |
US3424238A (en) * | 1967-05-08 | 1969-01-28 | Ritter Pfaudler Corp | Glassed heat exchanger construction |
US3481393A (en) * | 1968-01-15 | 1969-12-02 | Ibm | Modular cooling system |
US3627488A (en) * | 1969-07-07 | 1971-12-14 | Raytheon Co | Corrosion- and erosion-resistant material |
US4240257A (en) * | 1973-02-22 | 1980-12-23 | The Singer Company | Heat pipe turbo generator |
US3831664A (en) * | 1973-11-07 | 1974-08-27 | Boeing Co | Heat pipe interfaces |
US4274479A (en) * | 1978-09-21 | 1981-06-23 | Thermacore, Inc. | Sintered grooved wicks |
US4268850A (en) * | 1979-05-11 | 1981-05-19 | Electric Power Research Institute | Forced vaporization heat sink for semiconductor devices |
US4291546A (en) * | 1979-06-11 | 1981-09-29 | Alco Foodservice Equipment Company | Cold plate heat exchanger |
US4301771A (en) * | 1980-07-02 | 1981-11-24 | Dorr-Oliver Incorporated | Fluidized bed heat exchanger with water cooled air distributor and dust hopper |
FR2489490A1 (en) * | 1980-08-27 | 1982-03-05 | Commissariat Energie Atomique | COOLING APPARATUS HAVING RADIANT PANEL AND EVAPORATOR PANEL |
US4357907A (en) * | 1980-10-27 | 1982-11-09 | Rockwell International Corporation | Fluidized bed combustor with improved indirect heat exchanger units |
US4565242A (en) * | 1981-03-13 | 1986-01-21 | Kubota Ltd. | Heat accumulating material enclosing container and heat accumulating apparatus |
JPH06101524B2 (en) * | 1985-09-18 | 1994-12-12 | 株式会社東芝 | Cooling element for semiconductor element |
US4720981A (en) * | 1986-12-23 | 1988-01-26 | American Standard Inc. | Cooling of air conditioning control electronics |
US4756360A (en) * | 1987-03-25 | 1988-07-12 | Riley Stoker Corporation | Fluidized bed heat exchanger |
US4888961A (en) * | 1988-07-11 | 1989-12-26 | Lancer Corporation | Cold plate apparatus |
US4838346A (en) * | 1988-08-29 | 1989-06-13 | The United States Of America As Represented By The Administrator Of The National Aeronautics And Space Administration | Reusable high-temperature heat pipes and heat pipe panels |
US4929414A (en) * | 1988-10-24 | 1990-05-29 | The United States Of America As Represented By The Secretary Of The Air Force | Method of manufacturing heat pipe wicks and arteries |
US4884168A (en) * | 1988-12-14 | 1989-11-28 | Cray Research, Inc. | Cooling plate with interboard connector apertures for circuit board assemblies |
US4884169A (en) * | 1989-01-23 | 1989-11-28 | Technology Enterprises Company | Bubble generation in condensation wells for cooling high density integrated circuit chips |
US5484015A (en) * | 1993-12-03 | 1996-01-16 | Kyees; Melvin | Cold plate and method of making same |
JPH07225094A (en) * | 1994-02-10 | 1995-08-22 | Oomiya Kasei Kk | Submerged type heat exchanger |
US5647429A (en) * | 1994-06-16 | 1997-07-15 | Oktay; Sevgin | Coupled, flux transformer heat pipes |
AU706388B2 (en) * | 1995-09-13 | 1999-06-17 | Manitowoc Foodservice Group, Inc. | Apparatus for cooling fluids |
US5812372A (en) * | 1996-06-07 | 1998-09-22 | International Business Machines Corporation | Tube in plate heat sink |
US6111749A (en) * | 1996-09-25 | 2000-08-29 | International Business Machines Corporation | Flexible cold plate having a one-piece coolant conduit and method employing same |
FR2773941B1 (en) * | 1998-01-19 | 2000-04-21 | Ferraz | DI-PHASIC EXCHANGER FOR AT LEAST ONE ELECTRONIC POWER COMPONENT |
US6163073A (en) * | 1998-04-17 | 2000-12-19 | International Business Machines Corporation | Integrated heatsink and heatpipe |
AUPP502698A0 (en) * | 1998-08-04 | 1998-08-27 | Andale Repetition Engineering Pty. Limited | Beverage chiller |
US6253836B1 (en) * | 1999-05-24 | 2001-07-03 | Compaq Computer Corporation | Flexible heat pipe structure and associated methods for dissipating heat in electronic apparatus |
US6457515B1 (en) * | 1999-08-06 | 2002-10-01 | The Ohio State University | Two-layered micro channel heat sink, devices and systems incorporating same |
US6397944B1 (en) * | 2000-01-28 | 2002-06-04 | Lsi Logic Corporation | Heat dissipating apparatus and method for electronic components |
US6519955B2 (en) * | 2000-04-04 | 2003-02-18 | Thermal Form & Function | Pumped liquid cooling system using a phase change refrigerant |
US7004240B1 (en) * | 2002-06-24 | 2006-02-28 | Swales & Associates, Inc. | Heat transport system |
JP2002062083A (en) * | 2000-08-11 | 2002-02-28 | Komatsu Ltd | Temperature control equipment |
US7134484B2 (en) * | 2000-12-07 | 2006-11-14 | International Business Machines Corporation | Increased efficiency in liquid and gaseous planar device cooling technology |
CA2329408C (en) * | 2000-12-21 | 2007-12-04 | Long Manufacturing Ltd. | Finned plate heat exchanger |
WO2002074032A1 (en) * | 2001-03-02 | 2002-09-19 | Sanyo Electric Co., Ltd. | Electronic device |
KR100402788B1 (en) * | 2001-03-09 | 2003-10-22 | 한국전자통신연구원 | The heat pipe with woven-wire wick and straight wire wick |
US6381135B1 (en) * | 2001-03-20 | 2002-04-30 | Intel Corporation | Loop heat pipe for mobile computers |
ES2187280B1 (en) * | 2001-06-28 | 2004-08-16 | Lear Automotive (Eeds) Spain, S.L. | PRINTED CIRCUIT PLATE WITH ISOLATED METAL SUBSTRATE WITH INTEGRATED REFRIGERATION SYSTEM. |
US6536510B2 (en) * | 2001-07-10 | 2003-03-25 | Thermal Corp. | Thermal bus for cabinets housing high power electronics equipment |
EP1276362B1 (en) * | 2001-07-13 | 2006-02-01 | Lytron, Inc. | Flattened tube cold plate for liquid cooling electrical components |
US6711017B2 (en) * | 2001-07-17 | 2004-03-23 | Hitachi Kokusai Electric Inc. | Cooling apparatus for electronic unit |
US20030015316A1 (en) * | 2001-07-18 | 2003-01-23 | Kemal Burkay | Heat exchange tube having increased heat transfer area |
US6828675B2 (en) * | 2001-09-26 | 2004-12-07 | Modine Manufacturing Company | Modular cooling system and thermal bus for high power electronics cabinets |
US6942018B2 (en) * | 2001-09-28 | 2005-09-13 | The Board Of Trustees Of The Leland Stanford Junior University | Electroosmotic microchannel cooling system |
US6679315B2 (en) * | 2002-01-14 | 2004-01-20 | Marconi Communications, Inc. | Small scale chip cooler assembly |
US6942019B2 (en) * | 2002-03-25 | 2005-09-13 | Ltx Corporation | Apparatus and method for circuit board liquid cooling |
US7117930B2 (en) * | 2002-06-14 | 2006-10-10 | Thermal Corp. | Heat pipe fin stack with extruded base |
US6804117B2 (en) * | 2002-08-14 | 2004-10-12 | Thermal Corp. | Thermal bus for electronics systems |
JP3757200B2 (en) * | 2002-09-25 | 2006-03-22 | 株式会社日立製作所 | Electronic equipment with cooling mechanism |
US7078803B2 (en) * | 2002-09-27 | 2006-07-18 | Isothermal Systems Research, Inc. | Integrated circuit heat dissipation system |
US7156159B2 (en) * | 2003-03-17 | 2007-01-02 | Cooligy, Inc. | Multi-level microchannel heat exchangers |
AU2003286855A1 (en) * | 2002-11-01 | 2004-06-07 | Cooligy, Inc. | Method and apparatus for achieving temperature uniformity and hot spot cooling in a heat producing device |
US7806168B2 (en) * | 2002-11-01 | 2010-10-05 | Cooligy Inc | Optimal spreader system, device and method for fluid cooled micro-scaled heat exchange |
US6889755B2 (en) * | 2003-02-18 | 2005-05-10 | Thermal Corp. | Heat pipe having a wick structure containing phase change materials |
US6903929B2 (en) * | 2003-03-31 | 2005-06-07 | Intel Corporation | Two-phase cooling utilizing microchannel heat exchangers and channeled heat sink |
CA2425233C (en) * | 2003-04-11 | 2011-11-15 | Dana Canada Corporation | Surface cooled finned plate heat exchanger |
US7320178B2 (en) * | 2003-06-20 | 2008-01-22 | Imi Cornelius Inc. | Standoff for cold plate and cold plate made with the standoff |
US7363962B2 (en) * | 2003-08-04 | 2008-04-29 | Cleland Sales Corporation | Cold plate for beer dispensing tower |
US20050077030A1 (en) * | 2003-10-08 | 2005-04-14 | Shwin-Chung Wong | Transport line with grooved microchannels for two-phase heat dissipation on devices |
US7140420B2 (en) * | 2003-11-05 | 2006-11-28 | General Electric Company | Thermal management apparatus and uses thereof |
TWI240061B (en) * | 2004-02-16 | 2005-09-21 | Forward Electronics Co Ltd | Method for manufacturing heat collector |
JP2005229047A (en) * | 2004-02-16 | 2005-08-25 | Hitachi Ltd | Cooling system for electronic equipment, and the electronic equipment using same |
US20060011336A1 (en) * | 2004-04-07 | 2006-01-19 | Viktor Frul | Thermal management system and computer arrangement |
US7161803B1 (en) * | 2004-04-12 | 2007-01-09 | Heady Gregory S | Cooling system for an electronic display |
US7256999B1 (en) * | 2004-04-12 | 2007-08-14 | Frontline Systems | Heat collector plate for an electronic display |
US6989991B2 (en) * | 2004-05-18 | 2006-01-24 | Raytheon Company | Thermal management system and method for electronic equipment mounted on coldplates |
US7983042B2 (en) * | 2004-06-15 | 2011-07-19 | Raytheon Company | Thermal management system and method for thin membrane type antennas |
US7187549B2 (en) * | 2004-06-30 | 2007-03-06 | Teradyne, Inc. | Heat exchange apparatus with parallel flow |
US7134485B2 (en) * | 2004-07-16 | 2006-11-14 | Hsu Hul-Chun | Wick structure of heat pipe |
JP2006054351A (en) * | 2004-08-13 | 2006-02-23 | Fujitsu Ltd | Device for cooling semiconductor element |
US20060096738A1 (en) * | 2004-11-05 | 2006-05-11 | Aavid Thermalloy, Llc | Liquid cold plate heat exchanger |
US7079393B2 (en) * | 2004-11-16 | 2006-07-18 | International Business Machines Corporation | Fluidic cooling systems and methods for electronic components |
US7493693B2 (en) * | 2004-12-28 | 2009-02-24 | Jia-Hao Li | Method for fabricating multi-layer wick structure of heat pipe |
TWI275765B (en) * | 2005-01-28 | 2007-03-11 | Foxconn Tech Co Ltd | Wick structure, method of manufacturing the wick structure, and heat pipe |
TWI259895B (en) * | 2005-03-18 | 2006-08-11 | Foxconn Tech Co Ltd | Heat pipe |
TWI275766B (en) * | 2005-03-18 | 2007-03-11 | Foxconn Tech Co Ltd | Heat pipe |
JP2006294678A (en) * | 2005-04-06 | 2006-10-26 | Matsushita Electric Ind Co Ltd | Radiator and cooling device having the same |
US7578337B2 (en) * | 2005-04-14 | 2009-08-25 | United States Thermoelectric Consortium | Heat dissipating device |
JP4539425B2 (en) * | 2005-04-28 | 2010-09-08 | 日立電線株式会社 | Heat pipe heat sink and method for manufacturing the same |
US7293601B2 (en) * | 2005-06-15 | 2007-11-13 | Top Way Thermal Management Co., Ltd. | Thermoduct |
TW200700686A (en) * | 2005-06-16 | 2007-01-01 | Yuh Cheng Chemical Co Ltd | Heat pipe |
US7347249B2 (en) * | 2005-07-18 | 2008-03-25 | Asia Vital Components Co., Ltd. | Fixing device for a radiator |
US7673389B2 (en) * | 2005-07-19 | 2010-03-09 | International Business Machines Corporation | Cold plate apparatus and method of fabrication thereof with a controlled heat transfer characteristic between a metallurgically bonded tube and heat sink for facilitating cooling of an electronics component |
US7345287B2 (en) * | 2005-09-30 | 2008-03-18 | Applied Materials, Inc. | Cooling module for charged particle beam column elements |
US7520316B2 (en) * | 2005-10-05 | 2009-04-21 | Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. | Heat sink with heat pipes |
JP4665713B2 (en) * | 2005-10-25 | 2011-04-06 | 日立電線株式会社 | Internal grooved heat transfer tube |
US20070151709A1 (en) * | 2005-12-30 | 2007-07-05 | Touzov Igor V | Heat pipes utilizing load bearing wicks |
US20070158050A1 (en) * | 2006-01-06 | 2007-07-12 | Julian Norley | Microchannel heat sink manufactured from graphite materials |
US20070175614A1 (en) * | 2006-01-30 | 2007-08-02 | Jaffe Limited | Loop heat exchange apparatus |
TW200733856A (en) * | 2006-02-20 | 2007-09-01 | Sunonwealth Electr Mach Ind Co | Composite heat-dissipating module |
US7406999B2 (en) * | 2006-04-27 | 2008-08-05 | Delphi Technologies, Inc. | Capillary-assisted compact thermosiphon |
US8051905B2 (en) * | 2006-08-15 | 2011-11-08 | General Electric Company | Cooling systems employing fluidic jets, methods for their use and methods for cooling |
US7624791B2 (en) * | 2006-09-08 | 2009-12-01 | Advanced Energy Industries, Inc. | Cooling apparatus for electronics |
US20080078534A1 (en) * | 2006-10-02 | 2008-04-03 | General Electric Company | Heat exchanger tube with enhanced heat transfer co-efficient and related method |
US7641101B2 (en) * | 2006-10-10 | 2010-01-05 | International Business Machines Corporation | Method of assembling a cooling system for a multi-component electronics system |
US20080093052A1 (en) * | 2006-10-20 | 2008-04-24 | Foxconn Technology Co., Ltd. | Heat dissipation device with heat pipes |
US7564685B2 (en) * | 2006-12-29 | 2009-07-21 | Google Inc. | Motherboards with integrated cooling |
US7694727B2 (en) * | 2007-01-23 | 2010-04-13 | Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. | Heat dissipation device with multiple heat pipes |
US20080173430A1 (en) * | 2007-01-23 | 2008-07-24 | Foxconn Technology Co., Ltd. | Heat dissipation device with heat pipes |
US7753109B2 (en) * | 2007-05-23 | 2010-07-13 | Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. | Heat dissipation device with heat pipes |
CN201115256Y (en) * | 2007-06-15 | 2008-09-10 | 鸿富锦精密工业(深圳)有限公司 | Heat radiation device |
US7746640B2 (en) * | 2007-07-12 | 2010-06-29 | Fu Zhun Precision Industry (Shen Zhen) Co., Ltd. | Heat dissipation device with heat pipes |
KR100803282B1 (en) * | 2007-07-26 | 2008-02-13 | 박용수 | Heating apparatus using hot water and steam |
US7760502B2 (en) * | 2007-10-23 | 2010-07-20 | International Business Machines Corporation | Cooling system employing a heat exchanger with phase change material, and method of operation thereof |
JP4703633B2 (en) * | 2007-12-04 | 2011-06-15 | 株式会社東芝 | Cooling plate structure |
GB2460837B (en) * | 2008-06-10 | 2012-03-28 | Tarmac Building Products Ltd | Changing the temperature of a thermal load |
US8297343B2 (en) * | 2008-10-15 | 2012-10-30 | Tai-Her Yang | Heat absorbing or dissipating device with multi-pipe reversely transported temperature difference fluids |
TWI389600B (en) * | 2008-12-19 | 2013-03-11 | 私立中原大學 | Coaxial cooling and rapid conductive coil construction and molds with cobalt cooling and rapid conductive coil construction |
WO2012020453A1 (en) * | 2010-08-10 | 2012-02-16 | Empire Technology Development Llc | Improved fluid cooling |
US20120067548A1 (en) * | 2010-09-20 | 2012-03-22 | Siemens Industry, Inc. | Polymeric membrane for heat exchange applications and method of fabrication thereof |
-
2009
- 2009-03-19 TW TW098108854A patent/TW201036527A/en not_active IP Right Cessation
- 2009-09-21 US US12/586,324 patent/US20100236761A1/en not_active Abandoned
Also Published As
Publication number | Publication date |
---|---|
TWI372596B (en) | 2012-09-11 |
US20100236761A1 (en) | 2010-09-23 |
Similar Documents
Publication | Publication Date | Title |
---|---|---|
TWI302242B (en) | Liquid cooling jacket | |
CN101859738B (en) | Large-area liquid-cooled heat dissipation device | |
CN107567248A (en) | Liquid-cooling heat radiator | |
TW201036527A (en) | Large-area liquid-cooled heat-dissipation device | |
TW200821801A (en) | Case having phase-change heat dissipating device | |
TWM246988U (en) | Water-cooling apparatus for electronic devices | |
TWM612914U (en) | Liquid-cooling heat dissipation structure | |
US11758689B2 (en) | Vapor chamber embedded remote heatsink | |
TWM291195U (en) | Water-cooling heat dissipation system | |
TW200848994A (en) | Heat dissipation device | |
TWI808656B (en) | Liquid cooling device and liquid cooling system having the liquid cooling device | |
US11924995B2 (en) | Water cooling head with sparse and dense fins | |
TWM628154U (en) | Air-liquid dual cooling radiator for memory modules | |
CN109699164B (en) | Plate type heat pipe radiating shell | |
TW201124691A (en) | Heat dissipation device | |
TW200840464A (en) | Water-cooling heat spreader module for a display card | |
TW200741433A (en) | Liquid-cooling heat sink | |
TWI785409B (en) | Easily expanded liquid-cooled heat sink | |
CN213660387U (en) | Circuit board assembly and electronic equipment | |
TWI294763B (en) | Heat dissipation device | |
TWI276394B (en) | Integrated liquid cooling system | |
CN209914359U (en) | Extension plate type heat pipe | |
TWI343234B (en) | ||
TW200816908A (en) | Heat dissipation module | |
TW202239302A (en) | Liquid-cooling heat dissipation structure |
Legal Events
Date | Code | Title | Description |
---|---|---|---|
MM4A | Annulment or lapse of patent due to non-payment of fees |