JP2008292054A - Ebullient cooling device - Google Patents

Ebullient cooling device Download PDF

Info

Publication number
JP2008292054A
JP2008292054A JP2007137480A JP2007137480A JP2008292054A JP 2008292054 A JP2008292054 A JP 2008292054A JP 2007137480 A JP2007137480 A JP 2007137480A JP 2007137480 A JP2007137480 A JP 2007137480A JP 2008292054 A JP2008292054 A JP 2008292054A
Authority
JP
Japan
Prior art keywords
passage
refrigerant
tube
external fluid
vapor
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Granted
Application number
JP2007137480A
Other languages
Japanese (ja)
Other versions
JP4941100B2 (en
Inventor
Koji Tanaka
公司 田中
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Denso Corp
Original Assignee
Denso Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Denso Corp filed Critical Denso Corp
Priority to JP2007137480A priority Critical patent/JP4941100B2/en
Publication of JP2008292054A publication Critical patent/JP2008292054A/en
Application granted granted Critical
Publication of JP4941100B2 publication Critical patent/JP4941100B2/en
Expired - Fee Related legal-status Critical Current
Anticipated expiration legal-status Critical

Links

Images

Classifications

    • 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
    • F28D15/02—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 in which the medium condenses and evaporates, e.g. heat pipes
    • F28D15/0266—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 in which the medium condenses and evaporates, e.g. heat pipes with separate evaporating and condensing chambers connected by at least one conduit; Loop-type heat pipes; with multiple or common evaporating or condensing chambers
    • 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
    • F28F1/126—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 consisting of zig-zag shaped fins

Landscapes

  • Engineering & Computer Science (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • Mechanical Engineering (AREA)
  • General Engineering & Computer Science (AREA)
  • Life Sciences & Earth Sciences (AREA)
  • Sustainable Development (AREA)
  • Geometry (AREA)
  • Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
  • Cooling Or The Like Of Electrical Apparatus (AREA)

Abstract

<P>PROBLEM TO BE SOLVED: To provide an ebullient cooling device capable of improving radiating performance. <P>SOLUTION: In this ebullient cooling device comprising a refrigerant tank 3 storing a liquid refrigerant boiled by receiving the heat of a heating element 2, and a radiation core 4 in which refrigerant vapor boiled in the refrigerant tank 3 flows to perform heat exchange between the refrigerant vapor and cooling air, and to condense the refrigerant vapor, the radiation core 4 is provided with a tube 41 having a vapor passage 411 in which the refrigerant vapor boiled in the refrigerant tank 3 flows, and a condensation passage 412 for condensing the refrigerant vapor, a radiation fin 42 promoting the heat exchange between the refrigerant vapor and the cooling air is disposed on a region corresponding to the condensation passage 412 on the outer surface of the tube 41, and the radiation fin 42 is not disposed on a region corresponding to the vapor passage 411 on the outer surface of the tube 41. <P>COPYRIGHT: (C)2009,JPO&INPIT

Description

本発明は、冷媒の沸騰と凝縮の繰り返しによって発熱体を冷却する沸騰冷却装置に関する。   The present invention relates to a boiling cooling device that cools a heating element by repeated boiling and condensation of a refrigerant.

従来、内部に冷媒を貯留する冷媒槽と、冷媒槽に組み付けられる放熱コア部とで構成され、冷媒槽の側面に発熱体が取り付けられた沸騰冷却装置が提案されている（例えば、特許文献１および２参照）。このような沸騰冷却装置の放熱コア部は、冷媒槽で発熱体の熱を受けて沸騰した冷媒蒸気が流れ込む蒸気通路と、冷媒蒸気を凝縮させる凝縮通路とを有している。また、放熱コア部は、蒸気通路および凝縮通路を形成する複数本のチューブと、隣接するチューブ間に設けられる放熱フィンより構成されている。
特開２０００−２６０９１９号公報 特開２００３−４２６７１号公報 2. Description of the Related Art Conventionally, there has been proposed a boiling cooling device that includes a refrigerant tank that stores a refrigerant therein and a heat radiating core unit that is assembled to the refrigerant tank, and a heating element attached to a side surface of the refrigerant tank (for example, Patent Document 1). And 2). The heat dissipation core part of such a boiling cooling device has a vapor passage through which the refrigerant vapor boiled by receiving heat from the heating element in the refrigerant tank flows, and a condensing passage for condensing the refrigerant vapor. Further, the heat radiating core section is composed of a plurality of tubes forming a vapor passage and a condensing passage, and heat radiating fins provided between adjacent tubes.
JP 2000-260919 A JP 2003-42671 A

しかしながら、上記特許文献１および２に記載の沸騰冷却装置では、チューブの外表面における蒸気通路に対応する部位に、放熱フィンが配設されている。このため、蒸気通路内で冷媒蒸気が外部流体に冷却されて凝縮液となり、この凝縮液が蒸気通路を上昇する冷媒蒸気と干渉することにより、放熱コア部内での冷媒循環が阻害され、放熱性能が低下するという問題がある。   However, in the boiling cooling devices described in Patent Documents 1 and 2, the radiation fins are disposed in the portions corresponding to the steam passages on the outer surface of the tube. For this reason, the refrigerant vapor is cooled to an external fluid in the vapor passage to become a condensate, and this condensate interferes with the refrigerant vapor rising in the vapor passage, so that the refrigerant circulation in the heat radiating core is inhibited, and the heat dissipation performance. There is a problem that decreases.

本発明は、上記点に鑑み、放熱性能を向上させることができる沸騰冷却装置を提供することを目的とする。   An object of this invention is to provide the boiling cooling device which can improve heat dissipation performance in view of the said point.

上記目的を達成するため、本発明では、発熱体（２）の熱を受けて沸騰する液冷媒を貯留する冷媒槽（３）と、冷媒槽（３）で沸騰した冷媒蒸気が流れ込み、冷媒蒸気と外部流体との間で熱交換を行って冷媒蒸気を凝縮させる放熱コア部（４）とを備えた沸騰冷却装置であって、放熱コア部（４）は、冷媒槽（３）で沸騰した冷媒蒸気が流れ込む第１の通路（４１１）と、冷媒蒸気を凝縮させる第２の通路（４１２）とを有するチューブ（４１）を備えており、チューブ（４１）の外表面における第２の通路（４１２）に対応する部位には、冷媒蒸気と外部流体の間の熱交換を促進する放熱フィン（４２）が配設されており、チューブ（４１）の外表面における第１の通路（４１１）に対応する部位には、放熱フィン（４２）が配設されていないことを特徴としている。   In order to achieve the above object, in the present invention, the refrigerant tank (3) that stores the liquid refrigerant that boiled by the heat of the heating element (2), and the refrigerant vapor that boiled in the refrigerant tank (3) flow into the refrigerant tank. And a heat-dissipating core part (4) for condensing the refrigerant vapor by exchanging heat with the external fluid, wherein the heat-dissipating core part (4) boiled in the refrigerant tank (3) A tube (41) having a first passage (411) into which the refrigerant vapor flows and a second passage (412) for condensing the refrigerant vapor is provided, and a second passage (on the outer surface of the tube (41) ( 412) is provided with a radiation fin (42) that promotes heat exchange between the refrigerant vapor and the external fluid, and is provided in the first passage (411) on the outer surface of the tube (41). Radiation fins (42) are arranged at the corresponding parts. Is characterized that no.

このように、チューブ（４１）の外表面のうち冷媒蒸気を凝縮させる第２の通路（４１２）に対応する部位にのみ、放熱フィン（４２）を設けることにより、沸騰した冷媒蒸気が流れ込む第１の通路（４１１）内で冷媒蒸気が外部流体に冷却されて凝縮することを抑制することができる。このため、放熱コア部（４）内で冷媒循環が阻害されることを抑制し、放熱性能を向上させることが可能となる。   Thus, by providing the radiation fin (42) only in the portion corresponding to the second passage (412) for condensing the refrigerant vapor in the outer surface of the tube (41), the first refrigerant vapor that has boiled flows into the first surface. It is possible to suppress the refrigerant vapor from being cooled and condensed by the external fluid in the passage (411). For this reason, it is possible to suppress the refrigerant circulation from being inhibited in the heat radiating core portion (4), and to improve the heat radiating performance.

また、上記特徴の沸騰冷却装置において、第１の通路（４１１）および第２の通路（４１２）は、チューブ（４１）内で外部流体の流れ方向に並設され、かつ、第１の通路（４１１）が第２の通路（４１２）より外部流体の流れ方向（Ｘ２）下流側に設けられていてもよい。   In the boiling cooling device having the above characteristics, the first passage (411) and the second passage (412) are arranged in parallel in the flow direction of the external fluid in the tube (41), and the first passage ( 411) may be provided downstream of the second passage (412) in the flow direction (X2) of the external fluid.

放熱コア部（４）に供給される外部流体は、放熱コア部（４）を通過する際に冷媒蒸気の潜熱を吸収することで温度が上昇する。このため、チューブ（４１）における外部流体の流れ方向（Ｘ２）では、外部流体温度が外部流体流れ下流側より上流側の方が低くなり、その結果、外部流体流れ下流側より上流側の方が放熱量が大きくなる。したがって、第１の通路（４１１）を第２の通路（４１２）より外部流体の流れ方向（Ｘ２）下流側に設ける、すなわち冷媒蒸気を凝縮させる第２の通路（４１２）を第１の通路（４１１）より外部流体流れ上流側に配置することで、放熱性能をより向上させることが可能となる。   The external fluid supplied to the heat radiating core (4) rises in temperature by absorbing the latent heat of the refrigerant vapor when passing through the heat radiating core (4). For this reason, in the flow direction (X2) of the external fluid in the tube (41), the external fluid temperature is lower on the upstream side than the downstream side of the external fluid flow, and as a result, the upstream side is lower than the downstream side of the external fluid flow. Increases heat dissipation. Accordingly, the first passage (411) is provided downstream of the second passage (412) in the flow direction (X2) of the external fluid, that is, the second passage (412) for condensing the refrigerant vapor is provided in the first passage ( 411) It is possible to further improve the heat dissipation performance by disposing it on the upstream side of the external fluid flow.

また、上記特徴の沸騰冷却装置において、チューブ（４１）の外表面における第１の通路（４１１）に対応する部位には、外部流体流れの剥離を生じさせる形状の外部流体剥離手段（５）が設けられていてもよい。   Further, in the boiling cooling device having the above characteristics, an external fluid peeling means (5) having a shape that causes the separation of the external fluid flow is provided at a portion corresponding to the first passage (411) on the outer surface of the tube (41). It may be provided.

これによれば、外部流体剥離手段（５）の外部流体流れ下流側領域において、外部流体流れをチューブ（４１）の外表面から剥離させることができるので、第１の通路（４１１）内で冷媒蒸気が外部流体に冷却されることをより抑制できる。このため、冷媒循環が阻害されることをより抑制し、放熱性能をより向上させることが可能となる。   According to this, since the external fluid flow can be peeled from the outer surface of the tube (41) in the external fluid flow downstream region of the external fluid peeling means (5), the refrigerant in the first passage (411). It is possible to further suppress the vapor from being cooled by the external fluid. For this reason, it becomes possible to suppress that refrigerant circulation is inhibited and to improve heat dissipation performance more.

また、上記特徴の沸騰冷却装置において、放熱コア部（４）は、冷媒槽（３）および放熱コア部（４）の配置方向（Ｘ１）における冷媒槽（３）から遠い側の端部に配置され、放熱フィン（４２）に接合されるフィン押さえ部材（４４）を有しており、フィン押さえ部材（４４）には、外部流体流れの剥離を生じさせる形状の外部流体剥離手段（６１）が設けられていてもよい。   Further, in the boiling cooling device having the above characteristics, the heat radiating core (4) is disposed at an end portion on the side farther from the refrigerant tub (3) in the arrangement direction (X1) of the refrigerant tub (3) and the heat radiating core (4). And a fin pressing member (44) joined to the heat radiating fin (42), and the fin pressing member (44) has an external fluid peeling means (61) shaped to cause peeling of the external fluid flow. It may be provided.

これによれば、外部流体剥離手段（６１）の外部流体流れ下流側領域において、外部流体流れをチューブ（４１）の外表面から剥離させることができるので、第１の通路（４１１）内で冷媒蒸気が外部流体に冷却されることをより抑制できる。このため、冷媒循環が阻害されることをより抑制し、放熱性能をより向上させることが可能となる。   According to this, since the external fluid flow can be peeled from the outer surface of the tube (41) in the external fluid flow downstream region of the external fluid peeling means (61), the refrigerant in the first passage (411). It is possible to further suppress the vapor from being cooled by the external fluid. For this reason, it becomes possible to suppress that refrigerant circulation is inhibited and to improve heat dissipation performance more.

また、上記特徴の沸騰冷却装置において、チューブ（４１）の内部には、チューブ（４１）内を複数の通路状に区画して、チューブ（４１）内の凝縮面積を増大する凝縮面積増大部材（４１０）が設けられており、凝縮面積増大部材（４１０）によって、第１の通路（４１１）と第２の通路（４１２）とが区画形成されており、第２の通路（４１２）は、凝縮面積増大部材（４１０）によって区画される複数の通路状部分（４１２ｂ）を有していてもよい。   In the boiling cooling device having the above characteristics, the tube (41) has a condensing area increasing member (in which the inside of the tube (41) is partitioned into a plurality of passages to increase the condensing area in the tube (41)). 410), the first passage (411) and the second passage (412) are partitioned by the condensation area increasing member (410), and the second passage (412) is condensed. You may have a some channel | path-like part (412b) divided by the area increase member (410).

なお、この欄および特許請求の範囲で記載した各手段の括弧内の符号は、後述する実施形態に記載の具体的手段との対応関係を示すものである。   In addition, the code | symbol in the bracket | parenthesis of each means described in this column and the claim shows the correspondence with the specific means as described in embodiment mentioned later.

（第１実施形態）
以下、本発明の第１実施形態について図１〜図４に基づいて説明する。図１は本第１実施形態に係る沸騰冷却装置１を示す斜視図で、図２は図１のＡ−Ａ断面図である。なお、図２中の破線矢印は冷媒の流れを示している。 (First embodiment)
Hereinafter, a first embodiment of the present invention will be described with reference to FIGS. FIG. 1 is a perspective view showing a boiling cooling device 1 according to the first embodiment, and FIG. 2 is a cross-sectional view taken along line AA of FIG. In addition, the broken-line arrow in FIG. 2 has shown the flow of the refrigerant | coolant.

図１および図２に示すように、本実施形態の沸騰冷却装置１は、冷媒の沸騰と凝縮の繰り返しによって発熱体２を冷却するもので、内部に液状の冷媒（液冷媒）を貯留する冷媒槽３と、この冷媒槽３の表面に組み付けられる放熱コア部４とを備え、一体ろう付けにより製造される。発熱体２は、例えば電気自動車のインバータ回路を構成するＩＧＢＴモジュールであり、ボルト（図示せず）等により冷媒槽３の表面に密着して固定される。   As shown in FIGS. 1 and 2, the boiling cooling device 1 of the present embodiment cools the heating element 2 by repeating boiling and condensation of the refrigerant, and stores a liquid refrigerant (liquid refrigerant) therein. The tank 3 and the heat radiating core part 4 assembled on the surface of the refrigerant tank 3 are provided, and are manufactured by integral brazing. The heating element 2 is, for example, an IGBT module that constitutes an inverter circuit of an electric vehicle, and is fixed in close contact with the surface of the refrigerant tank 3 with bolts (not shown) or the like.

本実施形態では、冷媒槽３の上方側の面（以下、上面３ａという）に放熱コア部４が配置されており、冷媒槽３における上面３ａとは反対側の面である下面３ｂ（図２参照）に、発熱体２が配置されている。また、本実施形態の冷媒槽３は、その上面３ａが水平面と平行になるように配置されている。このため、冷媒槽３および放熱コア部４の設置方向（以下、設置方向Ｘ１という）は重力方向と一致している。   In the present embodiment, the heat radiating core portion 4 is disposed on the upper surface (hereinafter referred to as the upper surface 3a) of the refrigerant tank 3, and the lower surface 3b (FIG. 2) that is the surface opposite to the upper surface 3a in the refrigerant tank 3. The heating element 2 is arranged. Moreover, the refrigerant tank 3 of this embodiment is arrange | positioned so that the upper surface 3a may become parallel to a horizontal surface. For this reason, the installation direction (henceforth installation direction X1) of the refrigerant | coolant tank 3 and the thermal radiation core part 4 corresponds with the gravity direction.

放熱コア部４は、冷媒槽３の一面３ａ上に略直立して組み付けられる複数本のチューブ４１と、各チューブ４１の外表面に接合される波状の放熱フィン４２とを有している。チューブ４１は、内部を冷媒が流通する冷媒通路を形成するものである。   The heat radiating core portion 4 has a plurality of tubes 41 assembled substantially upright on the one surface 3 a of the refrigerant tank 3, and waved heat radiating fins 42 joined to the outer surface of each tube 41. The tube 41 forms a refrigerant passage through which the refrigerant flows.

図３は、本第１実施形態におけるチューブ４１を示す断面図である。図３に示すように、チューブ４１の内部には、インナーフィン４１０が挿入されている。このインナーフィン４１０は、熱伝導性に優れる薄い金属板（例えば、アルミニウム板）を所定のピッチで交互に折り曲げて波状に成形したもので、チューブ４１内の凝縮面積を増大させるとともに、チューブ４１内に後述する冷媒循環路を形成する目的で用いられる。なお、インナーフィン４１０が、本発明の凝縮面積増大部材に相当している。   FIG. 3 is a cross-sectional view showing the tube 41 in the first embodiment. As shown in FIG. 3, the inner fin 410 is inserted into the tube 41. The inner fin 410 is a thin metal plate (for example, an aluminum plate) excellent in thermal conductivity, which is alternately bent at a predetermined pitch and formed into a wave shape. The inner fin 410 increases the condensation area in the tube 41 and increases the inside of the tube 41. Are used for the purpose of forming a refrigerant circulation path to be described later. The inner fin 410 corresponds to the condensation area increasing member of the present invention.

インナーフィン４１０は、折り曲げ部（山部と谷部）の延設方向を重力方向（設置方向Ｘ１）に向けてチューブ４１内に挿入され、かつ、チューブ４１内の左下側に偏って配置され、各折り曲げ部がチューブ４１の内壁面に当接して、ろう付けされている。これにより、チューブ４１内には、インナーフィン４１０の右側に確保される蒸気通路４１１と、インナーフィン４１０の上側に確保される第１凝縮通路４１２ａと、インナーフィン４１０のピッチ間に形成される複数の第２凝縮通路４１２ｂが形成される。そして、蒸気通路４１１、第１凝縮通路４１２ａおよび第２凝縮通路４１２ｂで上記の冷媒循環路を構成している。本実施形態では、チューブ４１内の第１凝縮通路４１２ａの通路断面積は、放熱コア部４に送風される冷却風の流れ方向（以下、冷却風流れ方向Ｘ２という）全域で一定になっている。   The inner fin 410 is inserted into the tube 41 with the extending direction of the bent portion (mountain portion and trough portion) directed in the direction of gravity (installation direction X1), and is disposed biased to the lower left side in the tube 41, Each bent portion is in contact with the inner wall surface of the tube 41 and brazed. Thereby, in the tube 41, a steam passage 411 secured on the right side of the inner fin 410, a first condensation passage 412 a secured on the upper side of the inner fin 410, and a plurality of pitches formed between the inner fins 410. The second condensing passage 412b is formed. The steam circulation path 411, the first condensing path 412a, and the second condensing path 412b constitute the refrigerant circulation path. In the present embodiment, the passage cross-sectional area of the first condensing passage 412a in the tube 41 is constant throughout the flow direction of cooling air blown to the heat radiating core section 4 (hereinafter referred to as cooling air flow direction X2). .

なお、第１凝縮通路４１２ａおよび第２凝縮通路４１２ｂをまとめて凝縮通路４１２ともいう。また、蒸気通路４１１が本発明の第１の通路に相当しており、凝縮通路４１２が本発明の第２の通路に相当している。   The first condensing passage 412a and the second condensing passage 412b are collectively referred to as a condensing passage 412. The steam passage 411 corresponds to the first passage of the present invention, and the condensation passage 412 corresponds to the second passage of the present invention.

チューブ４１は、放熱フィン４２との接合面である両側面（外表面）が、冷却風流れ方向Ｘ２に沿って配置されるが、このとき、凝縮通路４１２が蒸気通路４１１より冷却風流れ上流側に位置するように、チューブ４１の向きを特定している。また、チューブ４１の、蒸気通路４１１と第１凝縮経路４１２ａとが接続する部位、すなわち蒸気通路４１１の冷媒槽３から遠い側の端部に対応する角部は、Ｒ形状になっている。   In the tube 41, both side surfaces (outer surfaces) that are joint surfaces with the radiation fins 42 are arranged along the cooling air flow direction X2, and at this time, the condensation passage 412 is upstream of the cooling air flow from the steam passage 411. The direction of the tube 41 is specified so that it may be located in FIG. Further, the portion of the tube 41 where the vapor passage 411 and the first condensation path 412a are connected, that is, the corner portion corresponding to the end portion of the vapor passage 411 on the side far from the refrigerant tank 3 has an R shape.

図２に戻り、冷媒槽３における発熱体２が固定された部位の上方側には、チューブ４１の蒸気通路４１１と連通し、発熱体２の熱を受けて沸騰した冷媒（冷媒蒸気）をチューブ４１内に流入させる冷媒蒸気入口３１が形成されている。また、冷媒槽３における冷媒蒸気入口３１の冷却風流れ上流側には、チューブ４１の凝縮通路４１２と連通し、チューブ４１内で凝縮した冷媒（液冷媒）を冷媒槽３に流入させる液冷媒出口３２が形成されている。   Returning to FIG. 2, on the upper side of the portion of the refrigerant tank 3 where the heating element 2 is fixed, the refrigerant (refrigerant vapor) boiled by receiving heat from the heating element 2 communicates with the vapor passage 411 of the tube 41. A refrigerant vapor inlet 31 is formed to flow into 41. Further, on the upstream side of the cooling air flow of the refrigerant vapor inlet 31 in the refrigerant tank 3, the liquid refrigerant outlet communicates with the condensation passage 412 of the tube 41 and allows the refrigerant (liquid refrigerant) condensed in the tube 41 to flow into the refrigerant tank 3. 32 is formed.

図４は、本第１実施形態における放熱コア部４を示す上面透過図である。図４に示すように、放熱フィン４２は、チューブ４１の外表面のうち、凝縮通路４１２に対応する部位にのみ設けられており、蒸気通路４１１に対応する部位には設けられていない。すなわち、チューブ４１の外表面のうち、チューブ４１の内部にインナーフィン４１０が配置されている部位には、放熱フィン４２が配設されており、チューブ４１の内部にインナーフィン４１０が配置されていない部位には、放熱フィン４２が配設されていない。   FIG. 4 is a top transparent view showing the heat radiating core portion 4 in the first embodiment. As shown in FIG. 4, the radiating fins 42 are provided only on the portion corresponding to the condensation passage 412 on the outer surface of the tube 41, and are not provided on the portion corresponding to the vapor passage 411. That is, in the outer surface of the tube 41, the heat radiating fins 42 are disposed at a portion where the inner fin 410 is disposed inside the tube 41, and the inner fin 410 is not disposed inside the tube 41. The heat radiating fins 42 are not provided at the site.

図１に戻り、放熱コア部４におけるチューブ４１の積層方向（以下、チューブ積層方向Ｘ３という）の両端部には、放熱フィン４２に接合され、上方側から放熱フィン４２を押さえるサイドプレート４３がそれぞれ配設されている。また、放熱コア部４における設置方向Ｘ１の冷媒槽３から遠い側（すなわち重力方向上方側）の端部には、放熱フィン４２に接合され、設置方向Ｘ１の冷媒槽３から遠い側から放熱フィン４２を押さえるアッパプレート４４が配設されている。なお、アッパプレート４４が、本発明のフィン押さえ部材に相当している。   Returning to FIG. 1, side plates 43 joined to the radiation fins 42 and holding the radiation fins 42 from above are respectively attached to both ends of the radiation core portion 4 in the lamination direction of the tubes 41 (hereinafter referred to as the tube lamination direction X3). It is arranged. Further, the end of the heat radiating core portion 4 on the side far from the refrigerant tank 3 in the installation direction X1 (that is, the upper side in the gravitational direction) is joined to the heat radiating fin 42, and An upper plate 44 that holds 42 is disposed. The upper plate 44 corresponds to the fin pressing member of the present invention.

次に、本実施形態の沸騰冷却装置１の作動を説明する。   Next, the operation of the boiling cooling device 1 of the present embodiment will be described.

図２に示すように、冷媒槽３に貯留される液冷媒は、発熱体２の熱を受けて沸騰し、冷媒蒸気となって冷媒蒸気入口３１を通ってチューブ４１の蒸気通路４１１内へ流入する。蒸気通路４１１を上昇して第１凝縮通路４１２ａ内に流入した冷媒蒸気の一部は、チューブ４１の内壁面に凝縮して液化し、残りの冷媒蒸気も第２凝縮通路４１２ｂ内でインナーフィン４１０の表面およびチューブ４１の内壁面に凝縮して液化する。第１、第２凝縮通路４１２ａ、４１２ｂ内で液化した冷媒は、液冷媒出口３２を通って冷媒槽３へ還流する。   As shown in FIG. 2, the liquid refrigerant stored in the refrigerant tank 3 is boiled by receiving heat from the heating element 2 and flows into the vapor passage 411 of the tube 41 through the refrigerant vapor inlet 31 as refrigerant vapor. To do. A part of the refrigerant vapor that rises up the vapor passage 411 and flows into the first condensation passage 412a condenses and liquefies on the inner wall surface of the tube 41, and the remaining refrigerant vapor also forms the inner fin 410 in the second condensation passage 412b. And condensed on the inner wall surface of the tube 41. The refrigerant liquefied in the first and second condensing passages 412a and 412b returns to the refrigerant tank 3 through the liquid refrigerant outlet 32.

以上説明したように、チューブ４１の外表面のうち冷媒蒸気を凝縮させる凝縮通路４１２に対応する部位にのみ放熱フィン４２を設けることにより、蒸気通路４１１内で冷媒蒸気が冷却風に冷却されて凝縮することを抑制することができる。このため、冷媒循環が阻害されることを抑制し、放熱性能を向上させることが可能となる。   As described above, by providing the radiation fins 42 only on the outer surface of the tube 41 corresponding to the condensation passage 412 for condensing the refrigerant vapor, the refrigerant vapor is cooled by the cooling air in the vapor passage 411 and condensed. Can be suppressed. For this reason, it becomes possible to suppress that a refrigerant circulation is inhibited and to improve heat dissipation performance.

また、チューブ４１の外表面のうち蒸気通路４１１に対応する部位には放熱フィン４２を配置しないため、チューブ４１における蒸気通路４１１の冷媒槽３から遠い側の端部に対応する角部を、Ｒ形状にすることができる。これにより、蒸気通路４１１の圧力損失を低減することができるため、冷媒循環を促進し、放熱性能をより向上させることが可能となる。   In addition, since the radiation fins 42 are not arranged in the portion corresponding to the vapor passage 411 in the outer surface of the tube 41, the corner portion corresponding to the end portion of the vapor passage 411 on the side far from the refrigerant tank 3 in the tube 41 is set to R. It can be shaped. Thereby, since the pressure loss of the vapor | steam path 411 can be reduced, it becomes possible to accelerate | stimulate refrigerant | coolant circulation and to improve heat dissipation performance more.

ところで、放熱コア部４に送風される冷却風は、放熱コア部４を通過する際に冷媒蒸気の潜熱を吸収することで温度が上昇する。このため、チューブ４１における冷却風流れ方向Ｘ２では、冷却風温度が冷却風流体流れ下流側より上流側の方が低くなり、その結果、冷却風流れ下流側より上流側の方が放熱量が大きくなる。したがって、凝縮通路４１２を蒸気通路４１１より冷却風流れ上流側に配置することで、放熱性能をさらに向上させることが可能となる。   By the way, the cooling air blown to the heat radiating core part 4 rises in temperature by absorbing the latent heat of the refrigerant vapor when passing through the heat radiating core part 4. For this reason, in the cooling air flow direction X2 in the tube 41, the cooling air temperature is lower on the upstream side than the downstream side of the cooling air fluid flow, and as a result, the heat release amount is higher on the upstream side than the downstream side of the cooling air flow. Become. Therefore, by disposing the condensing passage 412 on the upstream side of the cooling air flow from the steam passage 411, it is possible to further improve the heat dissipation performance.

（第２実施形態）
次に、本発明の第２実施形態について図５に基づいて説明する。上記第１実施形態と同様の部分については同一の符号を付して説明を省略する。図５は、本第２実施形態における放熱コア部４を示す上面透過図である。 (Second Embodiment)
Next, a second embodiment of the present invention will be described with reference to FIG. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted. FIG. 5 is a top transparent view showing the heat radiating core portion 4 in the second embodiment.

図５に示すように、複数本のチューブ４１の外表面における蒸気通路４１１に対応する部位には、チューブ積層方向Ｘ３に突出する断面半円状の突起部５が、の設置方向Ｘ１（重力方向）全域に亘って配設されている。この突起部５は、チューブ４１の外表面における蒸気通路４１１に対応する部位のうち、最も冷却風流れ上流側に配置されている。なお、突起部５が、本発明の外部流体剥離手段に相当している。   As shown in FIG. 5, in a portion corresponding to the steam passage 411 on the outer surface of the plurality of tubes 41, a projecting portion 5 having a semicircular cross section protruding in the tube stacking direction X <b> 3 has ) It is arranged over the entire area. The protrusion 5 is disposed on the most upstream side of the cooling air flow among the portions corresponding to the steam passage 411 on the outer surface of the tube 41. In addition, the protrusion part 5 is equivalent to the external fluid peeling means of this invention.

これにより、突起部５の冷却風流れ下流側領域において、冷却風流れをチューブ４１の外表面から剥離させることができるので、蒸気通路４１１内の冷媒蒸気が冷却風によって冷却されることをより抑制できる。このため、放熱コア部４内で冷媒循環が阻害されることをより抑制し、放熱性能をより向上させることが可能となる。   As a result, the cooling air flow can be separated from the outer surface of the tube 41 in the cooling air flow downstream region of the protrusion 5, thereby further suppressing the refrigerant vapor in the vapor passage 411 from being cooled by the cooling air. it can. For this reason, it is possible to further suppress the refrigerant circulation from being inhibited in the heat radiating core portion 4 and further improve the heat radiating performance.

また、突起部５を、チューブ４１の外表面における蒸気通路４１１に対応する部位のうち、最も冷却風流れ上流側に配置することで、放熱フィン４２の位置決めをすることが可能となる。   Further, by disposing the protrusion 5 on the most upstream side of the cooling air flow among the portions corresponding to the steam passage 411 on the outer surface of the tube 41, the radiation fins 42 can be positioned.

（第３実施形態）
次に、本発明の第３実施形態について図６〜図８に基づいて説明する。上記第１実施形態と同様の部分については同一の符号を付して説明を省略する。 (Third embodiment)
Next, a third embodiment of the present invention will be described with reference to FIGS. The same parts as those in the first embodiment are denoted by the same reference numerals and description thereof is omitted.

図６は本第３実施形態に係る沸騰冷却装置１を示す斜視図で、図７は本第３実施形態における放熱コア部４を冷却風流れ下流側から見た状態を示す拡大正面図で、図８は本第３実施形態における放熱コア部４を示す上面図である。   FIG. 6 is a perspective view showing the boiling cooling device 1 according to the third embodiment, and FIG. 7 is an enlarged front view showing a state in which the heat radiating core portion 4 in the third embodiment is viewed from the downstream side of the cooling air flow. FIG. 8 is a top view showing the heat radiating core portion 4 in the third embodiment.

図６〜図８に示すように、アッパプレート４４の冷却風流れ下流側の端部には、冷却風流れをチューブ４１の外表面から剥離させる剥離部材６１が設けられている。具体的には、剥離部材６１は、重力方向下方側（冷媒槽３側）に向かって延びる板状に形成されており、その冷却風流れ下流側の端部がチューブ４１の外表面および放熱フィン４２に接触するようになっている。また、剥離部材６１は、冷却風流れ上流側に向かうにつれてチューブ４１の外表面から遠ざかるように形成されている。隣接する剥離部材６１間には所定の隙間が設定されており、放熱コア部４を通過する冷却風の流れを妨げないようになっている。なお、剥離部材６１が、本発明の外部流体剥離手段に相当している。   As shown in FIGS. 6 to 8, a peeling member 61 that peels the cooling air flow from the outer surface of the tube 41 is provided at the end of the upper plate 44 on the downstream side of the cooling air flow. Specifically, the peeling member 61 is formed in a plate shape extending toward the lower side in the gravitational direction (the refrigerant tank 3 side), and the end portion on the downstream side of the cooling air flow is the outer surface of the tube 41 and the radiating fin. 42 is contacted. Further, the peeling member 61 is formed so as to move away from the outer surface of the tube 41 toward the upstream side of the cooling air flow. A predetermined gap is set between the adjacent peeling members 61 so as not to hinder the flow of cooling air passing through the heat radiating core portion 4. The peeling member 61 corresponds to the external fluid peeling means of the present invention.

また、隣接するチューブ４１間に配置された剥離部材６の下端部は、接続部材６２により接続されている。接続部材６２は、設置方向Ｘ１に直交する平面状に形成されており、そのチューブ積層方向Ｘ１両端部は、チューブ４１の外表面に接触するようになっている。また、接続部材６２の冷却風流れ上流側の端部は、放熱フィン４２と接触するようになっている。本実施形態では、剥離部材６１および接続部材６２は、アッパプレート４４と一体に成形されている。   Further, the lower end portion of the peeling member 6 disposed between the adjacent tubes 41 is connected by a connecting member 62. The connecting member 62 is formed in a planar shape orthogonal to the installation direction X1, and both ends of the tube stacking direction X1 are in contact with the outer surface of the tube 41. Further, the end of the connection member 62 on the upstream side of the cooling air flow is in contact with the heat radiation fins 42. In the present embodiment, the peeling member 61 and the connecting member 62 are formed integrally with the upper plate 44.

これにより、剥離部材６１の冷却風流れ下流側領域において、冷却風流れをチューブ４１の外表面から剥離させることができるので、蒸気通路４１１内の冷媒蒸気が冷却風によって冷却されることをより抑制できる。このため、放熱コア部４内で冷媒循環が阻害されることをより抑制し、放熱性能をより向上させることが可能となる。   Thereby, in the downstream area of the cooling air flow of the peeling member 61, the cooling air flow can be peeled from the outer surface of the tube 41, so that the refrigerant vapor in the vapor passage 411 is further suppressed from being cooled by the cooling air. it can. For this reason, it is possible to further suppress the refrigerant circulation from being inhibited in the heat radiating core portion 4 and further improve the heat radiating performance.

また、隣接するチューブ４１間に配置された剥離部材６を接続部材６２により接続することで、剥離部材６の強度を向上させることが可能となる。また、接続部材６２を、そのチューブ積層方向Ｘ１両端部がチューブ４１の外表面に接触するように形成することで、チューブピッチ（隣接するチューブ４１のチューブ積層方向Ｘ３の間隔）を規制することが可能となる。   Moreover, it becomes possible to improve the intensity | strength of the peeling member 6 by connecting the peeling member 6 arrange | positioned between the adjacent tubes 41 by the connection member 62. FIG. Further, by forming the connecting member 62 so that both ends of the tube stacking direction X1 are in contact with the outer surface of the tube 41, the tube pitch (interval of the tube stacking direction X3 of the adjacent tubes 41) can be regulated. It becomes possible.

（他の実施形態）
なお、上記各実施形態では、凝縮通路４１２を蒸気通路４１１より冷却風流れ上流側に配置した例について説明したが、これに限らず、蒸気通路４１１より冷却風流れ下流側に配置してもよい。 (Other embodiments)
In each of the above embodiments, the example in which the condensing passage 412 is disposed on the upstream side of the cooling air flow from the steam passage 411 has been described. However, the present invention is not limited thereto, and the condensing passage 412 may be disposed on the downstream side of the cooling air flow. .

また、上記各実施形態では、チューブ４１内の第１凝縮通路４１２の通路断面積を冷却風流れ方向Ｘ２全域で一定にした例について説明したが、これに限らず、図９（ａ）に示すように、冷却風流れ上流側に向かうにつれて、通路断面積が小さくなる、すなわちインナーフィン４１０の設置方向Ｘ１の長さが長くなるようにしてもよい。   Moreover, although each said embodiment demonstrated the example which made passage cross-sectional area of the 1st condensing passage 412 in the tube 41 constant in the cooling wind flow direction X2 whole area, it is not restricted to this, It shows to Fig.9 (a) As described above, the passage cross-sectional area may be reduced toward the upstream side of the cooling air flow, that is, the length of the installation direction X1 of the inner fin 410 may be increased.

第１凝縮通路４１２内においては、冷却風流れ上流側に向かうにつれて冷媒蒸気の量が少なくなるため、第１凝縮通路４１２の通路断面積を小さくしても特に問題はない。一方、第１凝縮通路４１２の通路断面積を小さくした分、インナーフィン４１０の長さを長くすることで、凝縮性能を向上させることができる。   In the first condensing passage 412, the amount of refrigerant vapor decreases toward the upstream side of the cooling air flow. Therefore, there is no particular problem even if the cross-sectional area of the first condensing passage 412 is reduced. On the other hand, the condensing performance can be improved by increasing the length of the inner fin 410 as much as the passage cross-sectional area of the first condensing passage 412 is reduced.

さらに、図９（ｂ）に示すように、蒸気通路４１１を設置方向Ｘ１に対して傾斜させることで、インナーフィン４１０の面積を増大させることができるため、凝縮性能をより向上させることができる。   Further, as shown in FIG. 9B, the area of the inner fin 410 can be increased by inclining the steam passage 411 with respect to the installation direction X1, and therefore the condensation performance can be further improved.

また、上記各実施形態は、上記した範囲以外にも、可能な範囲で適宜組み合わせてもよい。   Moreover, you may combine each said embodiment suitably in the possible range besides the above-mentioned range.

第１実施形態に係る沸騰冷却装置１を示す斜視図である。It is a perspective view showing boiling cooling device 1 concerning a 1st embodiment. 図１のＡ−Ａ断面図である。It is AA sectional drawing of FIG. 第１実施形態におけるチューブ４１を示す断面図である。It is sectional drawing which shows the tube 41 in 1st Embodiment. 第１実施形態における放熱コア部４を示す上面透過図である。It is an upper surface transmission figure which shows the thermal radiation core part 4 in 1st Embodiment. 第２実施形態における放熱コア部４を示す上面透過図である。It is an upper surface transmission figure which shows the thermal radiation core part 4 in 2nd Embodiment. 第３実施形態に係る沸騰冷却装置１を示す斜視図である。It is a perspective view which shows the boiling cooling device 1 which concerns on 3rd Embodiment. 第３実施形態における放熱コア部４を冷却風流れ下流側から見た状態を示す拡大正面図である。It is an enlarged front view which shows the state which looked at the thermal radiation core part 4 in 3rd Embodiment from the cooling air flow downstream. 第３実施形態における放熱コア部４を示す上面図である。It is a top view which shows the thermal radiation core part 4 in 3rd Embodiment. 他の実施形態としてのチューブ４１を示す断面図である。It is sectional drawing which shows the tube 41 as other embodiment.

符号の説明Explanation of symbols

２…発熱体、３…冷媒槽、４…放熱コア部、５…突起部（外部流体剥離手段）、４１…チューブ、４２…放熱フィン、６１…剥離部材（外部流体剥離手段）、４１０…インナーフィン（凝縮面積増大部材）、４１１…蒸気通路（第１の通路）、４１２…凝縮通路（第２の通路）、４１２ｂ…第２凝縮通路（通路状部分）。   DESCRIPTION OF SYMBOLS 2 ... Heat generating body, 3 ... Refrigerant tank, 4 ... Radiation core part, 5 ... Projection part (external fluid peeling means), 41 ... Tube, 42 ... Radiation fin, 61 ... Stripping member (external fluid peeling means), 410 ... Inner Fins (condensation area increasing members), 411... Steam passage (first passage), 412... Condensation passage (second passage), 412 b.

Claims (5)

発熱体（２）の熱を受けて沸騰する液冷媒を貯留する冷媒槽（３）と、
前記冷媒槽（３）で沸騰した冷媒蒸気が流れ込み、前記冷媒蒸気と外部流体との間で熱交換を行って前記冷媒蒸気を凝縮させる放熱コア部（４）とを備える沸騰冷却装置であって、
前記放熱コア部（４）は、前記冷媒槽（３）で沸騰した前記冷媒蒸気が流れ込む第１の通路（４１１）と、前記冷媒蒸気を凝縮させる第２の通路（４１２）とを有するチューブ（４１）を備えており、
前記チューブ（４１）の外表面における前記第２の通路（４１２）に対応する部位には、前記冷媒蒸気と前記外部流体の間の熱交換を促進する放熱フィン（４２）が配設されており、
前記チューブ（４１）の外表面における前記第１の通路（４１１）に対応する部位には、前記放熱フィン（４２）が配設されていないことを特徴とする沸騰冷却装置。 A refrigerant tank (3) for storing a liquid refrigerant that boiled by receiving heat from the heating element (2);
A boiling cooling device comprising: a heat radiating core (4) configured to condense the refrigerant vapor by flowing heat between the refrigerant vapor and an external fluid by flowing the refrigerant vapor boiled in the refrigerant tank (3). ,
The heat radiating core section (4) has a first passage (411) into which the refrigerant vapor boiled in the refrigerant tank (3) flows and a second passage (412) that condenses the refrigerant vapor ( 41)
A heat radiating fin (42) for promoting heat exchange between the refrigerant vapor and the external fluid is disposed at a portion corresponding to the second passage (412) on the outer surface of the tube (41). ,
The boiling cooling device characterized in that the radiating fin (42) is not disposed in a portion corresponding to the first passage (411) on the outer surface of the tube (41). 前記第１の通路（４１１）および前記第２の通路（４１２）は、前記チューブ（４１）内で前記外部流体の流れ方向に並設され、かつ、前記第１の通路（４１１）が前記第２の通路（４１２）より前記外部流体の流れ方向（Ｘ２）下流側に設けられていることを特徴とする請求項１に記載の沸騰冷却装置。 The first passage (411) and the second passage (412) are juxtaposed in the flow direction of the external fluid in the tube (41), and the first passage (411) is the first passage (411). 2. The boiling cooling device according to claim 1, wherein the boiling cooling device is provided on the downstream side in the flow direction (X2) of the external fluid from the two passages (412). 前記チューブ（４１）の外表面における前記第１の通路（４１１）に対応する部位には、前記外部流体流れの剥離を生じさせる形状の外部流体剥離手段（５）が設けられていることを特徴とする請求項１または２に記載の沸騰冷却装置。 A portion of the outer surface of the tube (41) corresponding to the first passage (411) is provided with external fluid peeling means (5) having a shape that causes the separation of the external fluid flow. The boiling cooling device according to claim 1 or 2. 前記放熱コア部（４）は、前記冷媒槽（３）および前記放熱コア部（４）の配置方向（Ｘ１）における前記冷媒槽（３）から遠い側の端部に配置され、前記放熱フィン（４２）に接合されるフィン押さえ部材（４４）を有しており、
前記フィン押さえ部材（４４）には、前記外部流体流れの剥離を生じさせる形状の外部流体剥離手段（６１）が設けられていることを特徴とする請求項１または２に記載の沸騰冷却装置。 The heat dissipating core part (4) is disposed at an end of the refrigerant tank (3) and the heat dissipating core part (4) in an arrangement direction (X1) on the side far from the refrigerant tank (3), and the heat dissipating fins ( 42) having a fin pressing member (44) to be joined to
The boiling cooling device according to claim 1 or 2, wherein the fin pressing member (44) is provided with an external fluid peeling means (61) configured to cause the external fluid flow to peel off. 前記チューブ（４１）の内部には、前記チューブ（４１）内を複数の通路状に区画して、前記チューブ（４１）内の凝縮面積を増大する凝縮面積増大部材（４１０）が設けられており、
前記凝縮面積増大部材（４１０）によって、前記第１の通路（４１１）と前記第２の通路（４１２）とが区画形成されており、
前記第２の通路（４１２）は、前記凝縮面積増大部材（４１０）によって区画される複数の通路状部分（４１２ｂ）を有していることを特徴とする請求項１ないし４のいずれか１つに記載の沸騰冷却装置。 Inside the tube (41), a condensing area increasing member (410) is provided for dividing the inside of the tube (41) into a plurality of passages and increasing the condensing area in the tube (41). ,
The first passage (411) and the second passage (412) are partitioned by the condensation area increasing member (410),
The said 2nd channel | path (412) has a some channel | path-like part (412b) divided by the said condensation area increasing member (410), Any one of Claim 1 thru | or 4 characterized by the above-mentioned. The boiling cooling apparatus according to 1.
JP2007137480A 2007-05-24 2007-05-24 Boiling cooler Expired - Fee Related JP4941100B2 (en)

Priority Applications (1)

Application Number Priority Date Filing Date Title
JP2007137480A JP4941100B2 (en) 2007-05-24 2007-05-24 Boiling cooler

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
JP2007137480A JP4941100B2 (en) 2007-05-24 2007-05-24 Boiling cooler

Publications (2)

Publication Number Publication Date
JP2008292054A true JP2008292054A (en) 2008-12-04
JP4941100B2 JP4941100B2 (en) 2012-05-30

Family

ID=40166962

Family Applications (1)

Application Number Title Priority Date Filing Date
JP2007137480A Expired - Fee Related JP4941100B2 (en) 2007-05-24 2007-05-24 Boiling cooler

Country Status (1)

Country Link
JP (1) JP4941100B2 (en)

Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62162847A (en) * 1986-01-10 1987-07-18 Toto Ltd Gas instantaneous type hot water supplier
JP2000260919A (en) * 1999-03-05 2000-09-22 Denso Corp Boiling/cooling device
JP2003028584A (en) * 2001-05-11 2003-01-29 Denso Corp Ebullient cooling apparatus
JP2004092942A (en) * 2002-08-29 2004-03-25 Denso Corp Heat exchanger

Patent Citations (4)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
JPS62162847A (en) * 1986-01-10 1987-07-18 Toto Ltd Gas instantaneous type hot water supplier
JP2000260919A (en) * 1999-03-05 2000-09-22 Denso Corp Boiling/cooling device
JP2003028584A (en) * 2001-05-11 2003-01-29 Denso Corp Ebullient cooling apparatus
JP2004092942A (en) * 2002-08-29 2004-03-25 Denso Corp Heat exchanger

Also Published As

Publication number Publication date
JP4941100B2 (en) 2012-05-30

Similar Documents

Publication Publication Date Title
TWI722736B (en) Heat sink
WO2017010536A1 (en) Cooling device
WO2019151291A1 (en) Heat sink
JPH0878588A (en) Boiling/cooling device
US20080093052A1 (en) Heat dissipation device with heat pipes
JP6358872B2 (en) Boiling cooler for heating element
WO2017047756A1 (en) Heat sink
JP5333161B2 (en) heatsink
US20080078529A1 (en) Cooling of the power components of a frequency converter
JP2013033807A (en) Cooling device and electronic apparatus using the same
JP2008025884A (en) Ebullient cooling type heat exchange device
JP2018133529A (en) Cooling device
JP4941100B2 (en) Boiling cooler
JP2009275945A (en) Ebullient cooling device
JP4877069B2 (en) Boiling cooler
JP6197651B2 (en) Cooling system
JP2017112189A (en) Thermo-siphon cooling device
WO2019168146A1 (en) Heat sink
JP2016205745A (en) Heat pipe type heat sink
JP2006234267A (en) Ebullient cooling device
JP2006229102A (en) Boiling cooler
JP2015140949A (en) Cooling device and data center including the same
JP2009250559A (en) Ebullient cooling device
JP5625835B2 (en) heat pipe
WO2013073696A1 (en) Cooling device and electronic device using same

Legal Events

Date Code Title Description
A621 Written request for application examination

Free format text: JAPANESE INTERMEDIATE CODE: A621

Effective date: 20090615

A977 Report on retrieval

Free format text: JAPANESE INTERMEDIATE CODE: A971007

Effective date: 20110525

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20110607

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20110628

A131 Notification of reasons for refusal

Free format text: JAPANESE INTERMEDIATE CODE: A131

Effective date: 20111115

A521 Written amendment

Free format text: JAPANESE INTERMEDIATE CODE: A523

Effective date: 20111216

TRDD Decision of grant or rejection written
A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

Effective date: 20120131

A01 Written decision to grant a patent or to grant a registration (utility model)

Free format text: JAPANESE INTERMEDIATE CODE: A01

A61 First payment of annual fees (during grant procedure)

Free format text: JAPANESE INTERMEDIATE CODE: A61

Effective date: 20120213

R151 Written notification of patent or utility model registration

Ref document number: 4941100

Country of ref document: JP

Free format text: JAPANESE INTERMEDIATE CODE: R151

FPAY Renewal fee payment (event date is renewal date of database)

Free format text: PAYMENT UNTIL: 20150309

Year of fee payment: 3

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

R250 Receipt of annual fees

Free format text: JAPANESE INTERMEDIATE CODE: R250

LAPS Cancellation because of no payment of annual fees