JPH06307782A - Radiator for flat heating element - Google Patents
Radiator for flat heating elementInfo
- Publication number
- JPH06307782A JPH06307782A JP12768293A JP12768293A JPH06307782A JP H06307782 A JPH06307782 A JP H06307782A JP 12768293 A JP12768293 A JP 12768293A JP 12768293 A JP12768293 A JP 12768293A JP H06307782 A JPH06307782 A JP H06307782A
- Authority
- JP
- Japan
- Prior art keywords
- heat
- thin tube
- tube container
- radiator
- group
- 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
Links
- 238000010438 heat treatment Methods 0.000 title claims description 48
- 230000005855 radiation Effects 0.000 claims abstract description 10
- 229910052751 metal Inorganic materials 0.000 claims abstract description 6
- 239000002184 metal Substances 0.000 claims abstract description 6
- 230000017525 heat dissipation Effects 0.000 claims description 22
- 239000007788 liquid Substances 0.000 claims description 17
- 238000001816 cooling Methods 0.000 claims description 16
- 230000032258 transport Effects 0.000 claims description 4
- 230000020169 heat generation Effects 0.000 claims description 2
- 238000000034 method Methods 0.000 abstract description 5
- 239000003507 refrigerant Substances 0.000 description 9
- 239000012530 fluid Substances 0.000 description 8
- 239000000853 adhesive Substances 0.000 description 7
- 230000001070 adhesive effect Effects 0.000 description 7
- 230000007423 decrease Effects 0.000 description 5
- 238000005452 bending Methods 0.000 description 3
- 238000009835 boiling Methods 0.000 description 3
- 238000009792 diffusion process Methods 0.000 description 3
- 238000010586 diagram Methods 0.000 description 2
- 230000000694 effects Effects 0.000 description 2
- 230000002349 favourable effect Effects 0.000 description 2
- 150000002739 metals Chemical class 0.000 description 2
- 238000011144 upstream manufacturing Methods 0.000 description 2
- 238000009423 ventilation Methods 0.000 description 2
- RYGMFSIKBFXOCR-UHFFFAOYSA-N Copper Chemical compound [Cu] RYGMFSIKBFXOCR-UHFFFAOYSA-N 0.000 description 1
- 229910052782 aluminium Inorganic materials 0.000 description 1
- XAGFODPZIPBFFR-UHFFFAOYSA-N aluminium Chemical compound [Al] XAGFODPZIPBFFR-UHFFFAOYSA-N 0.000 description 1
- 230000004323 axial length Effects 0.000 description 1
- 238000004891 communication Methods 0.000 description 1
- 230000000295 complement effect Effects 0.000 description 1
- 229910052802 copper Inorganic materials 0.000 description 1
- 239000010949 copper Substances 0.000 description 1
- 238000005259 measurement Methods 0.000 description 1
- 230000001737 promoting effect Effects 0.000 description 1
- 239000004065 semiconductor Substances 0.000 description 1
- 230000003068 static effect Effects 0.000 description 1
- 238000005728 strengthening Methods 0.000 description 1
- 230000005514 two-phase flow Effects 0.000 description 1
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
- 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
- F28D15/0233—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 the conduits having a particular shape, e.g. non-circular cross-section, annular
Landscapes
- Engineering & Computer Science (AREA)
- Life Sciences & Earth Sciences (AREA)
- Sustainable Development (AREA)
- Physics & Mathematics (AREA)
- Thermal Sciences (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Cooling Or The Like Of Semiconductors Or Solid State Devices (AREA)
Abstract
Description
【０００１】[0001]
【産業上の利用分野】本発明はヒートパイプ応用の平形
発熱体用放熱器に関するもので特に細管ヒーヒートパイ
プ群、ループ型及び非ループ型蛇行細管ヒートパイプ等
の有効利用に依り放熱を行なう平形発熱体用放熱器に関
する。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a radiator for a flat heating element applied to a heat pipe, and more particularly to a flat heating for effectively radiating heat from a group of thin tube heat-heat pipes, loop type and non-loop type meandering thin tube heat pipes. Body radiator
【０００２】[0002]
【従来の技術】図８、図９及び図１０は従来の蛇行細管
ヒートパイプ応用の平形発熱体用放熱器の構成の一例を
示す。図８は正面図、図９はその平面図、図１０は受熱
細管コンテナ群の整列状態を示す断面図である。受熱細
管コンテナ群１−１と断熱細管コンテナ群１−３及び放
熱細管コンテナ群１−２とからなる蛇行細管ヒートパイ
プ１の受熱細管コンテナ群１−１は複数層の平板状に密
接して整列されて、２枚の熱量授受板２の間に熱伝導性
良好な状態に接着挟持され放熱器の受熱部として構成さ
れてある。放熱手段ａの矢印は対流風を示し、放熱細管
コンテナ群１−２はその対流風の中で通風良好な状態に
展開されてある。熱量授受板２は該放熱器が対象とする
平形発熱体ｈと受熱細管コンテナ群１−１の間の熱量授
受を良好に仲介する為の熱拡散板の役目を兼ねている。
又１−４，１−５は蛇行細管コンテナの蛇行の為のター
ン部である。2. Description of the Related Art FIGS. 8, 9 and 10 show an example of the structure of a conventional radiator for a flat heating element applied to a meandering thin tube heat pipe. 8 is a front view, FIG. 9 is a plan view thereof, and FIG. 10 is a cross-sectional view showing an aligned state of the heat receiving thin tube container group. The heat receiving thin tube container group 1-1 of the meandering thin tube heat pipe 1 including the heat receiving thin tube container group 1-1, the heat insulating thin tube container group 1-3, and the heat radiating thin tube container group 1-2 is closely arranged in a plurality of flat plates. Then, the two heat quantity transfer plates 2 are bonded and sandwiched between the two heat quantity transfer plates 2 in a state of good heat conductivity to constitute a heat receiving portion of the radiator. The arrow of the heat radiating means a indicates convection air, and the heat radiating thin tube container group 1-2 is developed in a favorable ventilation state in the convection air. The heat quantity transfer plate 2 also serves as a heat diffusion plate for favorably mediating the heat quantity transfer between the flat heating element h and the heat receiving thin tube container group 1-1 targeted by the radiator.
Further, 1-4 and 1-5 are turn portions for meandering the meandering thin tube container.
【０００３】この様に構成された蛇行細管ヒートパイプ
応用の平形発熱体用放熱器において所定の面積の接着面
を有する平形発熱体ｈに発生した熱量は熱量授受板２に
より拡散されて２枚の熱量授受板２の片側の面により挟
持された部分の受熱細管コンテナ群１−１に吸収され、
この内部の作動液に核沸騰を発生せしめる。この核沸騰
の圧力波により作動液は蛇行細管ヒートパイプ１がルー
プ型であればループ内にて軸方向に振動しながら循環し
て熱量を放熱細管コンテナ群１−２に輸送する。この熱
量輸送は蛇行細管ヒートパイプが非ループ型であれば作
動液の軸方向振動のみによって行なわれる。放熱細管コ
ンテナ群１−２に輸送された熱量は放熱手段ａにより対
流熱伝達により対流風中に放熱される。この様な放熱器
各部の作動により平形発熱体ｈは効率的に放熱冷却され
る。In the radiator for a flat heating element applied to the meandering thin tube heat pipe configured as described above, the amount of heat generated in the flat heating element h having an adhesive surface of a predetermined area is diffused by the heat quantity transfer plate 2 to form two sheets. The heat quantity transfer plate 2 is absorbed by the heat receiving thin tube container group 1-1 in the portion sandwiched by the surface on one side,
Nucleate boiling is generated in the working fluid inside. When the meandering thin tube heat pipe 1 is a loop type, the pressure wave of this nucleate boiling circulates while oscillating in the axial direction in the loop and transports the heat quantity to the heat radiating thin tube container group 1-2. If the meandering thin tube heat pipe is a non-loop type, this heat transfer is performed only by the axial vibration of the hydraulic fluid. The heat quantity transferred to the heat radiating thin tube container group 1-2 is radiated to the convective wind by the heat radiating means a by the convective heat transfer. The flat heating element h is efficiently radiated and cooled by the operation of each part of the radiator.
【０００４】放熱器の主たる構成要素である蛇行細管ヒ
ートパイプは長尺細管コンテナが受熱部と放熱部の間を
多数回往復蛇行することにより形成されてある。その作
動は総ての受熱部が相互に連通しているので、各受熱部
で発生する核沸騰とその圧力波は相互に補完し合いまた
相互に助長し合って、作動液の循環推進力と軸方向振動
エネルギーを増幅し活性化させるものであり、そのこと
は特願昭６２−１５５７４７号、特願平２−３１９４６
１号及び特願平３−６１３８５号に詳述されてある。The meandering thin tube heat pipe which is a main component of the radiator is formed by a long thin tube container meandering between the heat receiving portion and the heat radiating portion many times. Since all the heat receiving parts are in communication with each other in its operation, the nucleate boiling generated in each heat receiving part and its pressure wave complement each other and mutually promote each other, thereby promoting the circulation driving force of the working fluid. It is intended to amplify and activate axial vibration energy, which is disclosed in Japanese Patent Application Nos. 62-155747 and 2-31946.
No. 1 and Japanese Patent Application No. 3-61385.
【０００５】この様なヒートパイプ式放熱器はその機能
及び性能が蛇行細管ヒートパイプを適用する場合より低
下はするものの、通常の２相流細管ヒートパイプ群を適
用して構成されてあっても良く、その場合の構造は図
８、図９における蛇行細管コンテナのターン部１−４、
１−５が無くなるだけで細管コンテナ群は夫々独立した
細管ヒートパイプの整列体となる。この場合に発生する
問題点は図８、図９の例とほぼ同様である。この様なヒ
ートパイプ式放熱器の熱輸送能力は必然的に２枚の熱量
授受板２により狭持されてある細管コンテナ群１−１の
本数に依存し、蛇行ターン数に依存する。又受熱部の軸
方向長さにも依存し、これ等から必然的に平形発熱体ｈ
と熱量授受板２との接触面積に依存する。これらのこと
から所定の面積の接着面を有する平形発熱体ｈの単位面
積当り発熱量が大幅に増加する場合これに対応して放熱
器の能力の拡大せしめるには以下に述べる様な問題点が
発生するものであった。Although such a heat pipe type radiator has its function and performance deteriorated as compared with the case where the meandering thin tube heat pipe is applied, even if it is constituted by applying a normal two-phase flow thin tube heat pipe group. Good, the structure in that case is the turn portion 1-4 of the meandering thin tube container in FIGS.
The thin tube container group becomes an array of independent thin tube heat pipes only by eliminating 1-5. The problems that occur in this case are almost the same as in the examples of FIGS. The heat transport capacity of such a heat pipe radiator necessarily depends on the number of the thin tube container groups 1-1 sandwiched by the two heat quantity transfer plates 2, and on the number of meandering turns. It also depends on the axial length of the heat-receiving part, and from this, it is inevitable that the flat heating element h
Depends on the contact area between the heat transfer plate 2 and the heat transfer plate 2. From these facts, when the amount of heat generated per unit area of the flat heating element h having an adhesive surface of a predetermined area is significantly increased, the following problems can be solved in order to expand the capability of the radiator. It happened.
【０００６】[0006]
（１）所定の面積の接着面を有する平形発熱体ｈから受
熱することの可能な受熱細管コンテナの配設本数には限
界がある。即ちその配設幅を平形発熱体ｈの接着面の幅
を大きく越えて拡大せしめても受熱することの可能な受
熱細管コンテナの本数は増加しない。また密接して整列
される細管コンテナは細管直径を大きくすれば本数が減
少し、本数を増加せしめるには細管直径を小さくする必
要があり、結果として所定の面積の接着面を有する平形
発熱体ｈからの受熱量には自ら限界が発生するものであ
った。(1) There is a limit to the number of heat receiving thin tube containers that can receive heat from the flat heating element h having an adhesive surface of a predetermined area. In other words, the number of heat-receiving thin tube containers capable of receiving heat does not increase even if the width of the arrangement is expanded greatly beyond the width of the bonding surface of the flat heating element h. Further, the number of closely arranged thin tube containers decreases as the diameter of the thin tubes increases, and it is necessary to reduce the diameter of the thin tubes to increase the number of tubes. As a result, a flat heating element h having an adhesive surface of a predetermined area h There was a limit in the amount of heat received from the plant.
【０００７】（２）所定面積の接着面を有する平形発熱
体ｈと組み合わせ適用する熱量授受板２の熱量拡散能力
には限界があり、平形発熱体ｈより大幅に大きな面積の
熱量授受版２を適用すると熱拡散の為の熱抵抗が増加
し、この熱抵抗を小さくする為に熱量授受板２の肉厚を
増加せしめると、平形発熱体ｈと受熱細管コンテナ群１
−１との距離が増大しその為の熱抵抗が増加し、結局熱
量授受板２を大型化して受熱細管コンテナ群１−１の挟
持本数を増加せしめても放熱器の熱輸送能力を効率的に
増加させることは困難であった。(2) The calorific value transfer plate 2 applied in combination with the flat heating element h having an adhesive surface of a predetermined area has a limit in the calorific value diffusing capacity, and the calorific value transfer plate 2 having a significantly larger area than the flat heating element h is used. When applied, the heat resistance for heat diffusion increases, and if the wall thickness of the heat quantity transfer plate 2 is increased to reduce this heat resistance, the flat heating element h and the heat receiving thin tube container group 1
Even if the distance from -1 increases and the heat resistance for that increases, and eventually the heat transfer plate 2 is enlarged and the number of the heat-receiving thin tube container groups 1-1 is increased, the heat transfer capacity of the radiator is efficient. It was difficult to increase.
【０００８】（３）熱量授受板２により整列狭持される
受熱細管コンテナ群１−１の層数を増加せしめても熱輸
送能力を強化する為の効果が少ない点も問題点であっ
た。又平形発熱体ｈの装着を片側のみに実施した場合に
該放熱器は加熱側の半分のみが作動し、性能が半減する
ことも問題点であった。これ等の原因は、熱量授受板２
により加えられる熱量の６０〜７０％は平形発熱体ｈに
近い受熱細管コンテナ群１−１の第１層で吸収され放熱
されることに困るものであり、第２層以降を作動させる
熱量は細管コンテナ壁の熱伝導のみによるもので、接触
熱抵抗によりその熱量は、順次大幅に減少する。第２層
に伝達される熱量はは第１層の３０〜４０％、第３層に
到達する熱量はは第１層の９〜１６％に過ぎないものと
なり、第４層以下には受放熱細管コンテナ群を作動せし
めるに必要な熱量は殆ど到達することが出来ない。(3) Even if the number of layers of the heat receiving thin tube container group 1-1 aligned and sandwiched by the heat quantity transfer plate 2 is increased, the effect of strengthening the heat transport capacity is small, which is also a problem. Further, when the flat heating element h is mounted on only one side, only half of the heating side of the radiator operates and the performance is halved. The cause of these is the heat exchange plate 2
60 to 70% of the amount of heat added by is absorbed by the first layer of the heat receiving thin tube container group 1-1 close to the flat heating element h and is radiated, and the amount of heat for operating the second and subsequent layers is small. This is due only to the heat conduction of the container wall, and the amount of heat decreases gradually due to the contact thermal resistance. The amount of heat transferred to the second layer is 30 to 40% of that of the first layer, and the amount of heat reaching the third layer is only 9 to 16% of that of the first layer. The amount of heat required to operate the thin tube container group can hardly reach.
【０００９】（４）平形発熱体用放熱器は一般に平形発
熱体ｈと交互に積層して使用される。従ってその放熱手
段ａとしての冷却対流の流れ方向は通常図８の矢印の如
く実施される。その様な場合、放熱量を増大させる為熱
量授受板２を大型化し、受熱細管コンテナ群１−１及び
放熱細管コンテナ群１−２を増加せしめることは細管列
数の増加を意味する。この場合は放熱手段ａの冷却対流
における流れの風下に至るほど熱交換流体温度が上昇す
るので、追加分細管コンテナの放熱能力は極めて悪くな
り、細管コンテナの追加による放熱能力向上の効果は極
めて少ないと云う問題があった。(4) The radiator for the flat heating element is generally used by alternately stacking with the flat heating element h. Therefore, the flow direction of the cooling convection as the heat radiating means a is usually carried out as shown by the arrow in FIG. In such a case, increasing the amount of heat transfer plate 2 in order to increase the amount of heat radiation and increasing the number of heat-receiving thin tube container groups 1-1 and the number of heat-radiating thin tube container groups 1-2 means an increase in the number of thin tube rows. In this case, since the heat exchange fluid temperature rises further downwind of the cooling convection of the heat radiating means a, the heat radiating ability of the additional capillary tube container becomes extremely poor, and the effect of improving the heat radiating ability by adding the thin tube container is extremely small. There was a problem called.
【００１０】（５）同様に放熱量を増大させる為熱量授
受板２を大型化し、受熱細管コンテナ群１−１の本数及
び放熱細管コンテナ群１−２の本数を増加せしめること
は細管列数の増加を意味し、このことは冷却対流の圧力
損失を増加せしめ静圧の増加を意味するもので、場合に
よっては放熱器に取って致命的な問題点となることもあ
った。(5) Similarly, increasing the amount of heat transfer plate 2 to increase the amount of heat radiation and increasing the number of heat-receiving thin tube container groups 1-1 and the number of heat-radiating thin tube container groups 1-2 are related to the number of thin tube rows. This means an increase, which means an increase in the pressure loss of the cooling convection and an increase in the static pressure, which may be a fatal problem for the radiator in some cases.
【００１１】（６）細管コンテナ群が蛇行細管コンテナ
で形成されてある場合熱量授受板２の片辺側に図９に例
示の如き受放熱に全く寄与することの無い比較的大型の
ターン部１−５を形成する必要があり、このターン部は
機械的外力に対して脆弱であり放熱器の取り扱いに注意
を必要とし、また商品価値を損なうものとして問題点の
一つとなっていた。(6) When the thin tube container group is formed of a meandering thin tube container One side of the heat quantity transfer plate 2 has a relatively large turn portion 1 as shown in FIG. It is necessary to form -5, and this turn part is vulnerable to mechanical external force, requires careful handling of the radiator, and is one of the problems that impairs the commercial value.
【００１２】本発明が解決しようとする課題は上述の
（１）〜（６）の問題点を解決することにあり、これに
より小さな接着面積であるにも拘らず強力な熱量を発生
する平形発熱体をも効率的に冷却することの出来る新規
な構造の細管ヒートパイプ式放熱器を提供する。The problem to be solved by the present invention is to solve the above-mentioned problems (1) to (6), whereby a flat heat generation which generates a strong amount of heat in spite of a small bonding area. (EN) Provided is a thin tube heat pipe type radiator having a novel structure capable of efficiently cooling the body.
【００１３】[0013]
【課題を解決する為の手段】図１、図２及び図３は本発
明の蛇行細管ヒートパイプ応用の平形発熱体用放熱器の
構成の一例を示す。この例に於ては放熱器が放熱対象と
する発熱体の熱量は金属間熱伝導により受熱細管コンテ
ナ群に吸収され、然る後放熱部細管コンテナ群に輸送さ
れた熱量は空気の対流熱伝達により放熱器系外の空気中
に放熱される方式になっている。本実施例以外の方式と
しては受放熱部共に金属間熱伝導を適用する方式、受放
熱部共に対流空気の熱伝達を適用する方式、受放熱部の
何れか一方には液体対流の熱伝達を適用し他方には対流
空気の熱伝達を適用する方式等がある。図１は正面図、
図２はその平面図、図３は受熱部内に於ける受熱細管コ
ンテナ群の整列状態を示す断面図である。受熱細管コン
テナ群１−１と断熱細管コンテナ群１−３及び放熱細管
コンテナ群１−２とからなる蛇行細管ヒートパイプ１の
受熱細管コンテナ群１−１は整列されて、２校の熱量授
受板２の間に熱伝導性良好な状態に接着挟持され放熱器
の受熱部として構成されてある。放熱手段ａの矢印は対
流風を示し、放熱細管コンテナ群１−２はその対流風の
中で通風良好な状態に展開されてある。熱量授受板２は
この放熱器が対象とする所定の面積の接着面を有する平
形発熱体ｈと受熱細管コンテナ群１−１の間の熱量授受
を良好に仲介する為の熱拡散板の役目を兼ねている。又
１−４，１−５は蛇行細管コンテナの蛇行の為のターン
部である。FIG. 1, FIG. 2 and FIG. 3 show an example of the configuration of a radiator for a flat heating element to which a meandering thin tube heat pipe of the present invention is applied. In this example, the heat quantity of the heating element that the radiator dissipates is absorbed by the heat-receiving thin tube container group due to heat conduction between metals, and the heat quantity transferred to the heat-dissipating thin tube container group after that is the convective heat transfer of air. The heat is dissipated in the air outside the radiator system. As a method other than this embodiment, a method of applying intermetallic heat conduction to both the heat receiving and radiating section, a method of applying heat transfer of convective air to both the heat receiving and radiating section, and heat transfer of liquid convection to either one of the heat receiving and radiating section. The other is the method of applying heat transfer of convection air. 1 is a front view,
2 is a plan view thereof, and FIG. 3 is a cross-sectional view showing an aligned state of the heat receiving thin tube container group in the heat receiving portion. The heat receiving thin tube container group 1-1 of the meandering thin tube heat pipe 1 including the heat receiving thin tube container group 1-1, the heat insulating thin tube container group 1-3, and the heat radiating thin tube container group 1-2 is aligned, and the heat quantity transfer plates of the two schools are arranged. It is bonded and sandwiched between the two in a state of good thermal conductivity and is configured as a heat receiving portion of the radiator. The arrow of the heat radiating means a indicates convection air, and the heat radiating thin tube container group 1-2 is developed in a favorable ventilation state in the convection air. The heat quantity transfer plate 2 functions as a heat diffusion plate for satisfactorily mediating the heat quantity transfer between the flat heating element h having an adhesive surface of a predetermined area and the heat receiving thin tube container group 1-1 targeted by the radiator. Also serves as. Further, 1-4 and 1-5 are turn portions for meandering the meandering thin tube container.
【００１４】図１及び図２に於ては本発明の平形発熱体
用放熱器の構成は外観的には図８及び図９の従来型の蛇
行細管ヒートパイプ応用の平形発熱体用放熱器と全く同
じであり、各構成部分の作用はほぼ同じである。各構成
部分の番号及び名称も同じである。従って図１及び図２
に於ける各部分の作用の説明は省略する。1 and 2, the structure of the radiator for a flat heating element according to the present invention is similar to that of the conventional radiator for a flat heating element of FIG. 8 and FIG. They are exactly the same, and the operation of each component is almost the same. The numbers and names of the respective components are also the same. Therefore, FIG. 1 and FIG.
The description of the operation of each part in the above is omitted.
【００１５】然し図１及び図２に於ては熱量授受板２の
構造、受熱細管コンテナ群１−１の整列状態、放熱細管
コンテナ群１−２の整列状態、受放熱部に於ける細管コ
ンテナの断面形状、には問題点解決の為の手段が実施さ
れてあり従来型の放熱器とは全く異なった構成になって
いる。図３は受熱部の断面図であって熱量授受板２によ
る細管コンテナ群１−１の挟持状態を示すと共に受熱細
管コンテナ群１−１の整列状態を示している。図３は従
来の放熱器の受熱部の断面を示す図１０とは全く異なっ
て居り、問題点解決の為の手段の実施状態が明示されて
ある。実施されてある問題点解決の為の手段は以下の通
りである。However, in FIGS. 1 and 2, the structure of the heat quantity transfer plate 2, the heat receiving thin tube container group 1-1 aligned state, the heat radiating thin tube container group 1-2 aligned state, and the thin tube container in the heat radiating portion. The cross-sectional shape of (1) has means for solving the problem, and has a completely different structure from the conventional radiator. FIG. 3 is a cross-sectional view of the heat receiving portion, showing a state of sandwiching the thin tube container group 1-1 by the heat exchange plates 2 and an aligned state of the heat receiving thin tube container group 1-1. FIG. 3 is completely different from FIG. 10 showing the cross section of the heat receiving portion of the conventional radiator, and clearly shows the implementation state of means for solving the problem. The means for solving the problems that have been implemented are as follows.
【００１６】（１）蛇行細管ヒートパイプ１の細管コン
テナは少なくとも受熱部及び放熱部においてはその断面
形状が長方形又は長円形であるように成形されてあるこ
と。 （２）受熱部及び、又は放熱部における受・放熱細管コ
ンテナ群１−１、１−２と、放熱器が対象とする発熱体
ｈ及び放熱手段ａとの間の熱量の授受は、受・放熱細管
コンテナ群の何れか又は双方と伝熱良好な状態に接続さ
れてある熱量授受板２を介してなされるよう構成されて
あること。 （３）熱量授受板２は熱伝導性の良好な金属で形成され
てあり、その受・放熱細管コンテナ群と接続される側の
面には、その全長に亙り、熱量授受板２の板面に直立す
る平板フィン群２−１が、細管コンテナの軸方向に平行
並列に形成されてあること。 （４）そのフィン間隙には、フィン２−１の側面と細管
コンテナの断面形状における長辺又は長径に相当する面
とが、フィン２−１の全長に亙って相互に密着している
状態に各細管コンテナが圧入接続されてあること。 （５）熱量授受板２の他の面には放熱器が対象とする発
熱体ｈまたは放熱手段ａに対する熱量授受手段が設けら
れてあること。(1) The thin tube container of the meandering thin tube heat pipe 1 is formed such that at least the heat receiving portion and the heat radiating portion have a rectangular or oval cross-sectional shape. (2) Transfer of the amount of heat between the heat-receiving part and / or the heat-receiving / radiating thin-tube container groups 1-1 and 1-2 in the heat-dissipating part and the heat-generating body h and the heat-dissipating means a targeted by the heat-dissipating device. It is configured to be performed via a heat quantity transfer plate 2 which is connected to either or both of the heat dissipation thin tube container groups in a good heat transfer state. (3) The heat quantity transfer plate 2 is formed of a metal having good heat conductivity, and the surface of the heat quantity transfer plate 2 on the side connected to the receiving and radiating thin tube container group extends over its entire length. The flat plate fin group 2-1 standing upright is formed in parallel and parallel to the axial direction of the thin tube container. (4) In the fin gap, the side surface of the fin 2-1 and the surface corresponding to the long side or the long diameter in the cross-sectional shape of the thin tube container are in close contact with each other over the entire length of the fin 2-1. Each thin tube container is press-fitted and connected to. (5) On the other surface of the heat quantity transfer plate 2, heat quantity transfer means for the heating element h or the heat dissipation means a targeted by the radiator is provided.
【００１７】[0017]
（１）細管コンテナの断面形状が長方形又は長円形であ
り、その短辺又は短径に相当する面が熱量授受板２の平
面に対向するよう配列されるから単位面積当たりの細管
コンテナ配設本数が増加し、平板フィン群２−１の形成
ににより細管コンテナの配設可能な幅が縮小するにも拘
らず一層当たりの配設本数は減少しない。 （２）平板フィン群２−１の金属間熱伝導により、発熱
体ａから吸収された熱量は熱量授受板２の深層に至る迄
極めて少ない熱損失で到達し、深層に配設されてある受
熱細管コンテナ群１−１に対する場合でも熱量を効率よ
く伝達する。これにより本発明の蛇行細管ヒートパイプ
式放熱器は熱量授受板２の面積を発熱体ｈの接着部面積
よりそれ程拡大することなく、熱量授受板２により積層
挟持される受熱細管コンテナ群１−１の積層数を増加せ
しめることにより、細管コンテナ挟持本数を大幅に増加
せしめることが可能になり、大容量放熱器を構成するこ
とが可能になる。また逆に熱量授受板２が放熱側として
適用されてある場合でも上述と同様に熱量授受板２の深
層に配設されてある放熱細管コンテナ群１−２から効率
よく熱量を引き出して放熱せしめることが可能になるか
ら、熱量授受板２により積層挟持される放熱細管コンテ
ナ群１−２の挟持本数を大幅に増加せしめて、大容量放
熱器を構成することが可能になる。このことは本発明が
解決しようとする問題点（１）項〜（３）項が完全に解
決されることを意味する。(1) Since the cross-sectional shape of the thin tube container is rectangular or oval, and the surfaces corresponding to the short sides or short diameters thereof are arranged to face the plane of the heat transfer plate 2, the number of thin tube containers arranged per unit area However, although the width in which the thin tube container can be arranged is reduced by forming the flat plate fin group 2-1, the number of arranged thin tubes cannot be further reduced. (2) Due to the metal-to-metal heat conduction of the flat plate fin group 2-1, the amount of heat absorbed from the heating element a reaches the deep layer of the heat quantity transfer plate 2 with a very small heat loss, and the heat received in the deep layer is received. Even in the case of the thin tube container group 1-1, the amount of heat is efficiently transmitted. Accordingly, in the meandering thin tube heat pipe type radiator of the present invention, the heat receiving thin tube container group 1-1 is sandwiched and sandwiched by the heat amount transferring plates 2 without the area of the heat transferring plates 2 being much larger than the area of the bonding portion of the heating element h. By increasing the number of stacked layers, it is possible to significantly increase the number of thin tube container sandwiches, and it is possible to configure a large-capacity radiator. On the contrary, even when the heat quantity transfer plate 2 is applied on the heat radiation side, the heat quantity can be efficiently extracted and radiated from the heat dissipation thin tube container group 1-2 arranged in the deep layer of the heat quantity transfer plate 2 as described above. Therefore, it is possible to significantly increase the number of heat radiation thin tube container groups 1-2 sandwiched and stacked by the heat quantity transfer plates 2 to form a large-capacity radiator. This means that the problems (1) to (3) to be solved by the present invention are completely solved.
【００１８】（３）放熱部の放熱手段が外気との対流熱
伝達方式である場合、細管コンテナの断面形状が長方形
または長円形に成形されてある本発明の放熱器は、放熱
細管コンテナ群１−２の展開整列の状態を調整すること
に依って、放熱部における対流流体の流れ状態を制御し
たり圧力損失を制御することが可能である。図４はその
ような放熱細管コンテナ群１−２の展開整列の状態の一
例を示す。図においては放熱細管コンテナ群１−２の各
細管コンテナの断面の長辺に相当する部分が対流の主流
の流れ方向に対して所定の角度をなす様に展開整列され
てあることを特徴としている。また図４に於ては対流の
主流ａ−１が放熱部の上流側正面及び両側面から低温対
流ａ−２として流入し、放熱細管コンテナ群１−２から
熱量を吸収して、高温対流ａ−３として放熱部の下流側
背面中央部から排出される様に、放熱細管コンテナ群１
−２の中心線を対称軸として左右対象の角度をなす２群
に整列展開されてある。この様に整列された放熱細管コ
ンテナ群１−２の列は、対流に対する上流側の細管コン
テナ群も下流側の細管コンテナ群も一様に低温対流によ
り冷却されて、従来の放熱器の如く、上流側の細管コン
テナ群で熱吸収して高温になった対流により下流側の細
管コンテナ群の放熱効率が低下する如き問題点が発生す
ることが無い。また対流の主流の流れ方向に対する細管
コンテナに与えられる所定の角度を小さくすることによ
り流体抵抗を減少せしめ対流の圧力損失を低下させるこ
とも可能である。このことは本発明が解決しようとする
問題点（４）項及び（５）項が完全に解決されることを
意味する。(3) When the heat radiating means of the heat radiating portion is a convective heat transfer system with the outside air, the radiator of the present invention in which the cross-sectional shape of the thin tube container is rectangular or oval, is It is possible to control the flow state of the convective fluid and the pressure loss in the heat radiating portion by adjusting the state of expansion and alignment of -2. FIG. 4 shows an example of such a state in which the heat radiating thin tube container group 1-2 is developed and aligned. In the figure, a portion corresponding to the long side of the cross section of each thin tube container of the heat radiation thin tube container group 1-2 is developed and aligned so as to form a predetermined angle with respect to the flow direction of the convection main stream. . Further, in FIG. 4, the main convection flow a-1 flows in as a low temperature convection flow a-2 from the front side and both side faces of the heat radiating portion, absorbs the amount of heat from the heat radiating thin tube container group 1-2, and becomes a high temperature convection flow a. As shown in FIG. 3, the heat radiating thin tube container group 1 is discharged so as to be discharged from the central portion on the downstream side of the heat radiating portion.
-2 is aligned and developed into two groups forming a symmetrical angle with the center line of -2 as the axis of symmetry. In the row of the heat-dissipating thin tube container group 1-2 arranged in this way, both the upstream thin tube container group and the downstream thin tube container group with respect to the convection are uniformly cooled by the low temperature convection, and like the conventional radiator, There is no problem that the heat dissipation efficiency of the downstream thin tube container group decreases due to the convection that has become high temperature by absorbing heat in the upstream thin tube container group. It is also possible to reduce the fluid resistance and the pressure loss of convection by reducing the predetermined angle given to the thin tube container with respect to the flow direction of the main flow of convection. This means that the problems (4) and (5) to be solved by the present invention are completely solved.
【００１９】（４）受熱細管コンテナ群１−１、１−２
は何れも断面形状が長方形または長円形であるから、従
来の真円形状に比較して屈曲作業が容易であり、蛇行の
為の屈曲を小さな曲率半径で実施することが出来る。即
ち図１、図２、及び図５に示されてある屈曲部１−４、
１−５は図８及び図９に示されてある従来例より大幅に
小型化されてある。特に部分拡大図、図５に詳細に示さ
れてある如く本発明の場合の曲げ方向は熱量授受版の平
面に平行な面内で屈曲されるから、熱量授受板の厚さ方
向に積層されることが無いので、屈曲部１−５が受熱部
の両平面より突出することが無く、放熱器の取り扱いが
容易になる。このことは本発明が解決しようとする問題
点（６）項が殆ど解決されることを意味する。(4) Heat receiving thin tube container group 1-1, 1-2
Since each of them has a rectangular or oval cross-sectional shape, bending work is easier than the conventional perfect circular shape, and bending for meandering can be performed with a small radius of curvature. That is, the bent portions 1-4 shown in FIGS. 1, 2 and 5,
1-5 is much smaller than the conventional example shown in FIGS. 8 and 9. Particularly, as shown in detail in a partially enlarged view and FIG. 5, the bending direction in the case of the present invention is bent in a plane parallel to the plane of the heat quantity transfer plate, so that the heat quantity transfer plates are laminated in the thickness direction. Since the bent portion 1-5 does not project from both planes of the heat receiving portion, the radiator can be easily handled. This means that the problem (6) to be solved by the present invention is almost solved.
【００２０】以上に詳述した各作用により本発明の細管
ヒートパイプ応用の平形発熱体用放熱器は従来の同方式
放熱器の問題点のすべてを解決することが出来る。With the above-described operations, the radiator for a flat heating element using the thin tube heat pipe of the present invention can solve all the problems of the conventional radiator of the same system.
【００２１】[0021]
第一実施例 長辺２．３ｍｍ短辺２．３ｍｍの長方形断面形状の無酸
素銅細管を長さ３５０ｍｍ毎に２８８回のターンを繰り
返す長尺の細管コンテナに作動液としてＨＣＦＣ１４２
ｂを封入した蛇行細管ヒートパイプ１を細管ヒートパイ
プ群として適用し、図１〜図５に説明されてある如き本
発明の平形発熱体用放熱器を構成した。二枚の熱量授受
板２は純アルミＡ１０５０を用いて形成し、それらの厚
さは３．４ｍｍ，幅２００ｍｍ，長さ１２０ｍｍであ
り、それらは夫々の内側面に直立して設けられてある各
１９枚の高さ７．６ｍｍ幅３．４ｍｍの熱量授受フィン
群２−１により夫々３６列、４層、１４４本の受熱部細
管コンテナ群１−１を密に加圧挟持して構成した。細管
ヒートパイプ群の他の部分の長さ１８０ｍｍは図１及び
図２に例示の如く展開されて放熱部細管コンテナ群１−
２として、対流放熱部を構成した。その配列は図４に例
示の如く、３６列、８段、２８８本であり、各細管の長
辺が対流ａの流れ方向に対して所定の角度をなすよう整
列され、対流制御機能が与えられた。First Example An oxygen-free copper thin tube having a rectangular cross-section with a long side of 2.3 mm and a short side of 2.3 mm is used as a working fluid in a long thin tube container in which 288 turns are repeated every 350 mm in length as a working fluid.
The meandering thin tube heat pipe 1 enclosing b was applied as a thin tube heat pipe group to construct a radiator for a flat heating element of the present invention as described in FIGS. 1 to 5. The two heat quantity transfer plates 2 are formed by using pure aluminum A1050, and have a thickness of 3.4 mm, a width of 200 mm, and a length of 120 mm, each of which is provided upright on the inner surface thereof. The heat quantity transfer fin group 2-1 having a height of 7.6 mm and a width of 3.4 mm was used to tightly press and sandwich 36 rows, 4 layers, and 144 heat receiving section thin tube container groups 1-1, respectively. The length 180 mm of the other part of the thin tube heat pipe group is expanded as illustrated in FIG. 1 and FIG.
2, the convection heat dissipation part was comprised. The arrangement is, as illustrated in FIG. 4, 36 rows, 8 stages and 288 lines, and the long sides of each thin tube are aligned so as to form a predetermined angle with respect to the flow direction of the convection a, and a convection control function is provided. It was
【００２２】この放熱器の電接面２−２に直径１００ｍ
ｍの円盤形状の平形発熱体ｈを加圧接触せしめ熱量１５
００Ｗを熱入力せしめ、放熱部には４０℃の空気を５ｍ
／ｓにて強制対流せしめて放熱能力を調べた。各部の機
能は前述の作用の項で説明した通りに作用し、電接面の
平衡温度は６７℃に留まり、周囲温度からの温度上昇は
２７℃、全熱抵抗値は０．０１８℃／Ｗと従来の細管ヒ
ートパイプ放熱器では得られなかった様な高性能測定値
が得られた。この性能は発熱体が半導体素子である場合
の温度上昇に極めて大きな余裕率を与え長期の寿命を保
証するものである。図９及び図１０に例示の如き従来型
の構造に構成した場合、このような細管ヒートパイプの
本数、熱量授受板の大きさでは、熱抵抗値は０．０２５
℃／Ｗが限界であり、電接面の平衡温度を７７．５℃以
下に引き下げることは不可能であった。またこの放熱器
の強制対流５ｍ／ｓにおける対流風の圧力損失は僅かに
６ｍｍＨ２Ｏであり、従来型放熱器の圧力損失が１０ｍ
ｍＨ２Ｏであったのに対して４０％も低下した。このこ
とは冷却ファンに対する負担を軽減せしめ、ファンの故
障発生率を大幅に低下せしめることを意味する。The electric contact surface 2-2 of this radiator has a diameter of 100 m.
Heat quantity of the disk-shaped flat heating element h of m
Heat input of 00W, and heat of 40 ° C for 5m
Forced convection was conducted at / s to examine the heat dissipation ability. The function of each part works as explained in the section of the above action, the equilibrium temperature of the electrical contact surface remains at 67 ° C, the temperature rise from the ambient temperature is 27 ° C, and the total thermal resistance is 0.018 ° C / W. And the high performance measurement value that was not obtained by the conventional thin tube heat pipe radiator was obtained. This performance gives a very large margin to the temperature rise when the heating element is a semiconductor element and guarantees a long life. In the case of the conventional structure as illustrated in FIGS. 9 and 10, the thermal resistance value is 0.025 when the number of such thin tube heat pipes and the size of the heat transfer plate are set.
Since the limit was ° C / W, it was impossible to lower the equilibrium temperature of the electric contact surface to 77.5 ° C or lower. Further, the pressure loss of the convection wind at the forced convection of 5 m / s of this radiator is only 6 mmH 2 O, and the pressure loss of the conventional radiator is 10 m.
It was 40% lower than that of mH 2 O. This means that the load on the cooling fan is reduced and the failure occurrence rate of the fan is significantly reduced.
【００２３】第二実施例 本実施例に於ては放熱部細管コンテナ群は第一実施例の
如く展開されることなく、図６に例示の如く、受熱部細
管コンテナ群と全く同一の構造に構成され、熱量授受フ
ィン群が設けられた熱量授受板３により加圧挟持して構
成されてある。従って放熱部細管コンテナ群の熱量は強
制対流によらず金属間熱伝導により極めて低い熱抵抗で
熱量授受板３の熱量放熱面２−３に至るまで輸送され
る。熱量放熱面２−３に輸送された熱量は、熱量放熱面
２−３に外接して設けられてある液冷ジャケット４によ
り冷媒液４−１内に放出され放熱器の系外に運搬され
る。図に於て６−１は冷媒液供給口であり６−２はその
排出口である。Second Embodiment In this embodiment, the heat dissipating section thin tube container group is not developed as in the first embodiment, but has the same structure as the heat receiving section thin tube container group as illustrated in FIG. It is configured to be pressed and sandwiched by the heat quantity transfer plate 3 provided with the heat quantity transfer fin group. Therefore, the heat quantity of the heat radiating section thin tube container group is transported to the heat quantity radiating surface 2-3 of the heat quantity transfer plate 3 with an extremely low heat resistance by the heat conduction between the metals regardless of the forced convection. The heat quantity transferred to the heat quantity radiating surface 2-3 is released into the refrigerant liquid 4-1 by the liquid cooling jacket 4 provided outside the heat quantity radiating surface 2-3 and is carried to the outside of the radiator. . In the figure, 6-1 is a refrigerant liquid supply port and 6-2 is its discharge port.
【００２４】このように構成された放熱部の放熱は金属
間熱伝導及び冷媒液の強制対流によりなされる放熱であ
るから、空気の強制対流熱伝導による放熱に比較して一
桁高い熱伝達率で放熱されるから放熱効率が極めて高
く、放熱部を大幅に小型高性能化することが出来る。The heat dissipation of the heat dissipating unit constructed in this manner is heat dissipation by intermetallic heat conduction and forced convection of the refrigerant liquid, so that the heat transfer coefficient is an order of magnitude higher than heat dissipation by forced convection heat conduction of air. Since the heat is dissipated in, the heat dissipation efficiency is extremely high, and the heat dissipation part can be made significantly smaller and have higher performance.
【００２５】第二実施例を更に小型高性能化するには液
冷ジャケット４を熱量授受板３に作り込むと良い。図７
はその構造を例示するもので３−１は液冷ジャケット部
である。To further reduce the size and improve the performance of the second embodiment, the liquid cooling jacket 4 may be built in the heat transfer plate 3. Figure 7
Shows the structure, and 3-1 is a liquid cooling jacket part.
【００２６】本実施例に於て熱量授受板３の熱量放熱面
２−３に至るまで輸送された熱量の放熱器系外に対する
放熱は必ずしも冷媒液の強制対流による放熱のみには限
定されない。熱量授受板３の熱量放熱面２−３に直接形
成されてある放熱フィン群、またはに外接して装着され
たヒートシンクの放熱フィン群による空気の対流放熱で
あっても良い。この場合は冷媒液の強制対流による放熱
の、高い熱伝達率の利用は出来なくなり、冷媒液による
放熱の場合より性能は低下するが、放熱部細管コンテナ
１−２の表面から、熱量授受板３の熱量放熱面２−３に
至る間の金属間熱伝導による良好な熱伝達が利用される
ので、放熱部の構造が小型化されかつ簡素化することが
出来る。In the present embodiment, the amount of heat transferred to the heat amount radiating surface 2-3 of the heat amount transfer plate 3 to the outside of the radiator system is not necessarily limited to the heat release by forced convection of the refrigerant liquid. Convection heat dissipation of air may be performed by the heat dissipation fin group formed directly on the heat quantity heat dissipation surface 2-3 of the heat quantity transfer plate 3 or the heat dissipation fin group of the heat sink mounted externally to the heat dissipation plane. In this case, the high heat transfer coefficient of heat dissipation due to forced convection of the refrigerant liquid cannot be used, and the performance is lower than that of heat dissipation due to the refrigerant liquid. However, the heat quantity transfer plate 3 is transferred from the surface of the heat dissipation part thin tube container 1-2. Since good heat transfer due to intermetallic heat conduction between the heat quantity radiating surface 2-3 is used, the structure of the heat radiating portion can be downsized and simplified.
【００２７】[0027]
【発明の効果】上述の様に本発明の平形発熱体用放熱器
は熱量授受フィン群の作用により、受放熱部に於ける細
管コンテナ群の層数を増加せしめても、その受放熱部の
熱量授受効率が低下することが無いので、接着面が比較
的小さな平形発熱体を対象とする場合であっても細管コ
ンテナ群の層数を増加せしめて細管コンテナの本数を充
分に増加せしめ、強力な熱量の授受を可能にする。また
長円形状断面の細管コンテナはその配設段列数が如何に
増加してもその対流方向制御機能により、対流の風上側
の吸収熱量により風下側の細管コンテナ群の放熱効率が
低下することなく、かつ対流風の圧力損失も極めて少な
くなるから、この点からも授受熱量を充分に増加せしめ
ることが可能になる。As described above, in the radiator for a flat heating element according to the present invention, even if the number of layers of the thin tube container group in the heat receiving / radiating portion is increased by the action of the heat quantity transmitting / receiving fin group, the heat receiving / radiating portion is Since the heat transfer efficiency does not decrease, even when the flat heating element with a relatively small adhesive surface is targeted, the number of layers of the thin tube container group can be increased to sufficiently increase the number of thin tube containers and It enables the transfer of a large amount of heat. In addition, no matter how the number of rows of the thin tube containers with an oval cross section increases, the heat dissipation efficiency of the group of thin tube containers on the leeward side decreases due to the amount of heat absorbed on the windward side of the convection due to the convection direction control function. Also, since the pressure loss of the convection wind is extremely small, the heat transfer amount can be sufficiently increased from this point as well.
【図１】本発明の第一実施例の正面図である。FIG. 1 is a front view of a first embodiment of the present invention.
【図２】本発明の第一実施例の平面図である。FIG. 2 is a plan view of the first embodiment of the present invention.
【図３】本発明の第一実施例の受熱部内に於ける受熱部
細管コンテナ群の整列状態を示す断面図である。FIG. 3 is a cross-sectional view showing an aligned state of a heat receiving part thin tube container group in the heat receiving part of the first embodiment of the present invention.
【図４】本発明の第一実施例の放熱部に於ける放熱部細
管コンテナ群の展開状態を示す説明図である。FIG. 4 is an explanatory view showing a developed state of a heat radiating section thin tube container group in the heat radiating section of the first embodiment of the present invention.
【図５】本発明の第一実施例の受熱部端縁に於ける受熱
部細管コンテナ群のターン部の状態を示す説明図であ
る。FIG. 5 is an explanatory view showing a state of a turn part of the heat receiving part thin tube container group at the heat receiving part end edge of the first embodiment of the present invention.
【図６】本発明の第二実施例の適用例の説明図である。FIG. 6 is an explanatory diagram of an application example of the second embodiment of the present invention.
【図７】本発明の第二実施例の他の適用例の説明図であ
る。FIG. 7 is an explanatory diagram of another application example of the second embodiment of the present invention.
【図８】従来型の細管ヒートパイプ式平形発熱体用放熱
器を示す正面図である。FIG. 8 is a front view showing a conventional radiator for a thin tube heat pipe type flat heating element.
【図９】従来型の細管ヒートパイプ式平形発熱体用放熱
器を示す平面図である。FIG. 9 is a plan view showing a conventional radiator for a thin tube heat pipe type flat heating element.
【図１０】従来型の細管ヒートパイプ式平形発熱体用放
熱器の受熱部内ける細管コンテナ群の整列状態を示す断
面図である。FIG. 10 is a cross-sectional view showing an aligned state of a group of thin tube containers in a heat receiving part of a radiator for a conventional thin tube heat pipe type flat heating element.
１ 蛇行細管ヒートパイプ １−１ 受熱部細管コンテナ群 １−２ 放熱部細管コンテナ群 １−３ 断熱部細管コンテナ群 １−４ ターン部 １−５ ターン部 ２ 熱量授受板 ２−１ 熱量授受フィン ２−２ 発熱体接着面 ２−３ 放熱面 ３ 熱量授受板 ３−１ 液冷ジャケット部 ４ 液冷ジャケット ４−１ 冷媒液 ６−１ 冷媒液供給口 ６−２ 冷媒液排出口 ａ 対流 ａ−１ 対流の主流 ａ−２ 低温対流 ａ−３ 高温対流 ｈ 平形発熱体 1 Meandering thin tube heat pipe 1-1 Heat receiving part thin tube container group 1-2 Radiating part thin tube container group 1-3 Heat insulating part thin tube container group 1-4 Turn part 1-5 Turn part 2 Heat exchange plate 2-1 Heat exchange fin 2 -2 Heating element adhering surface 2-3 Radiating surface 3 Heat quantity transfer plate 3-1 Liquid cooling jacket part 4 Liquid cooling jacket 4-1 Refrigerant liquid 6-1 Refrigerant liquid supply port 6-2 Refrigerant liquid discharge port a Convection a-1 Mainstream of convection a-2 Low temperature convection a-3 High temperature convection h Flat heating element
Claims (5)
て密に且つ並列に整列されて形成されてある細管ヒート
パイプ層の複数層が積層されて、受熱細管コンテナ群と
断熱細管コンテナ群及び放熱細管コンテナ群が形成され
てあり、受熱細管コンテナ群で吸収した熱量を断熱細管
コンテナ群により中継して放熱細管コンテナ群に輸送し
放熱せしめる細管ヒートパイプ応用の平形発熱体用放熱
器であって、細管ヒートパイプの細管コンテナは少なく
とも受熱部及び放熱部においては、その断面形状が長方
形又は長円形であるように成形されてあり、受熱部及
び、又は放熱部における受・放熱細管コンテナ群と、放
熱器が対象とする発熱体及び放熱手段との間の熱量の授
受は、受・放熱細管コンテナ群の何れか又は双方を挟持
して伝熱良好な状態に接着されてある熱量授受板を介し
てなされるよう構成されてあり、この熱量授受板は熱伝
導性の良好な金属で形成されてあり、その受・放熱細管
コンテナ群を挟持する側の面には、その全長に亙り、熱
量授受板の板面に直立する平板フィン群が、細管コンテ
ナの軸方向に平行並列に形成されてあり、そのフィン間
隙には、フィンの側面と細管コンテナの断面形状におけ
る長辺に相当する面とが、フィンの全長に亙って相互に
密着している状態に各細管コンテナが圧入接続されてあ
り、熱量授受板の他の面には放熱器が対象とする所定の
発熱体または所定の放熱手段に対する熱量授受手段が設
けられてあることを特徴とする平形発熱体用放熱器。1. A heat-receiving thin tube container group and an adiabatic thin tube container group are formed by stacking a plurality of thin tube heat pipe layers in which thin tube heat pipe groups are densely and parallelly arranged in the same plane. And a heat dissipation thin tube container group is formed, and it is a radiator for flat heating element for thin tube heat pipe that relays the amount of heat absorbed by the heat receiving thin tube container group and transports it to the heat dissipation thin tube container group to radiate heat. The thin tube container of the thin tube heat pipe is formed such that at least the heat receiving section and the heat radiating section have a rectangular or oval cross-sectional shape, and the heat receiving section and / or the heat radiating thin tube container group in the heat radiating section The amount of heat exchanged between the heat generator and the heat dissipating means targeted by the radiator should be such that either or both of the receiving and radiating thin tube container groups are sandwiched to ensure good heat transfer. It is configured to be bonded via a bonded heat quantity transfer plate, and this heat quantity transfer plate is made of metal with good thermal conductivity, and is attached to the surface on the side that holds the heat receiving / radiating thin tube container group. Over its entire length, a group of flat plate fins that stand upright on the plate surface of the heat transfer plate is formed in parallel and parallel to the axial direction of the thin tube container, and the fin gap has a cross-sectional shape of the side surface of the fin and the thin tube container. The thin tube containers are press-fitted and connected in such a manner that the surface corresponding to the long side of each of the fins is in close contact with each other over the entire length of the fin, and the radiator is applied to the other surface of the heat transfer plate. A heat radiator for a flat heating element, which is provided with a heat quantity transfer means for a predetermined heat generating element or a predetermined heat radiating means.
ヒートパイプの長尺細管コンテナが受熱部と放熱部の間
を多数回往復蛇行して形成される蛇行細管コンテナの直
管部群が適用されてあることを特徴とする請求項１に記
載の平形発熱体用放熱器。2. A group of thin tube heat pipes is a group of straight tube portions of a meandering thin tube container formed by a long thin tube container of a meandering thin tube heat pipe being meandered many times between a heat receiving section and a heat radiating section. The radiator for a flat heating element according to claim 1, wherein
発熱手段に対する熱量授受手段は、放熱細管コンテナ群
と外気の間の対流熱伝達方式であって、放熱細管コンテ
ナ群は外気の対流内に展開せしめられてあり、且つその
断面形状における長辺に相当する面は対流の主流の流れ
方向に対して所定の角度を形成して整列せしめられてあ
ることを特徴とする請求項１に記載の平形発熱体用放熱
器。3. The heat transfer means for transferring heat to a predetermined heat generating means of the radiator in the heat radiating section is a convection heat transfer system between the heat radiating thin tube container group and the outside air, and the heat radiating thin tube container group is inside the convection of the outside air. 2. The surface according to claim 1, wherein the surface corresponding to the long side in the cross-sectional shape is aligned at a predetermined angle with respect to the flow direction of the main flow of convection. Radiator for flat heating element.
加熱・冷却手段に対する熱量授受手段は熱媒液の強制対
流であって、その面には熱量授受板に液冷用ジャケット
部が作り込まれてあるか、熱量授受板に外接して液冷用
ジャケットが装着されてあるかの何れかであることを特
徴とする請求項１に記載の平形発熱体用放熱器。4. The heat quantity transfer means for external heating / cooling means provided on the other surface of the heat quantity transfer plate is forced convection of a heat transfer medium, and the surface thereof has a liquid cooling jacket portion. The radiator for a flat heating element according to claim 1, which is either built in or has a liquid cooling jacket attached to the heat exchange plate.
加熱・冷却手段に対する熱量授受手段は強制対流風であ
って、その面には熱量授受板に空冷用放熱フィン群が形
成されてあるか、熱量授受板に外接して空冷用放熱フィ
ン群が装着されてあるかの何れかであることを特徴とす
る請求項１に記載の平形発熱体用放熱器。5. The heat quantity transfer means for the external heating / cooling means provided on the other surface of the heat quantity transfer plate is forced convection air, and a heat radiation plate group for air cooling is formed on the surface of the heat quantity transfer plate. The radiator for a flat heating element according to claim 1, wherein the radiator for heat generation is attached to the heat exchange plate, and a heat radiation fin group for air cooling is attached to the heat exchange plate.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12768293A JP3364758B2 (en) | 1993-04-20 | 1993-04-20 | Heat sink for flat heating element |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP12768293A JP3364758B2 (en) | 1993-04-20 | 1993-04-20 | Heat sink for flat heating element |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPH06307782A true JPH06307782A (en) | 1994-11-01 |
| JP3364758B2 JP3364758B2 (en) | 2003-01-08 |
Family
ID=14966107
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP12768293A Expired - Lifetime JP3364758B2 (en) | 1993-04-20 | 1993-04-20 | Heat sink for flat heating element |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JP3364758B2 (en) |
Cited By (5)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11132678A (en) * | 1997-10-27 | 1999-05-21 | Toshiba Corp | Power converter and heat pipe cooler for power converter |
| JP2008505305A (en) * | 2004-07-03 | 2008-02-21 | テラダイン・インコーポレーテッド | Micro heat pipe with wedge capillary |
| JP2009261125A (en) * | 2008-04-16 | 2009-11-05 | Denso Corp | Power control unit |
| CN110864571A (en) * | 2018-08-27 | 2020-03-06 | 新光电气工业株式会社 | Cooling device |
| CN120786752A (en) * | 2025-09-11 | 2025-10-14 | 杭州华源前线能源设备有限公司 | Electric heater |
-
1993
- 1993-04-20 JP JP12768293A patent/JP3364758B2/en not_active Expired - Lifetime
Cited By (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPH11132678A (en) * | 1997-10-27 | 1999-05-21 | Toshiba Corp | Power converter and heat pipe cooler for power converter |
| JP2008505305A (en) * | 2004-07-03 | 2008-02-21 | テラダイン・インコーポレーテッド | Micro heat pipe with wedge capillary |
| JP2009261125A (en) * | 2008-04-16 | 2009-11-05 | Denso Corp | Power control unit |
| CN110864571A (en) * | 2018-08-27 | 2020-03-06 | 新光电气工业株式会社 | Cooling device |
| CN120786752A (en) * | 2025-09-11 | 2025-10-14 | 杭州华源前线能源设备有限公司 | Electric heater |
| CN120786752B (en) * | 2025-09-11 | 2025-12-16 | 杭州华源前线能源设备有限公司 | electric heater |
Also Published As
| Publication number | Publication date |
|---|---|
| JP3364758B2 (en) | 2003-01-08 |
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