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JP2010114174A - Core structure for heat sink - Google Patents

Core structure for heat sink Download PDF

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JP2010114174A
JP2010114174A JP2008283929A JP2008283929A JP2010114174A JP 2010114174 A JP2010114174 A JP 2010114174A JP 2008283929 A JP2008283929 A JP 2008283929A JP 2008283929 A JP2008283929 A JP 2008283929A JP 2010114174 A JP2010114174 A JP 2010114174A
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plate
heat sink
members
core structure
oblique
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Joji Yamazaki
丈嗣 山崎
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T Rad Co Ltd
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T Rad Co Ltd
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Abstract

【課題】ヒートシンクの厚み方向における伝熱性の向上と、冷却液の攪拌促進と、による熱交換性能の向上をはかったヒートシンク用コア構造の提供。
【解決手段】第１プレート１，第２プレート２の幅方向に並列して多数の縦部材1a，縦部材2aを設けると共に、隣り合う各縦部材1a間，縦部材2a間を斜め部材1b，斜め部材2bで一体的に形成する。そして第１プレート１，第２プレート２を積層し、夫々の縦部材1a，縦部材2aを整合して重ね合わせると共に、第１プレート１の斜め部材1bと第２プレート２の斜め部材2bとは、流れ方向に互いに離間して且つその向きを逆向きにする。
【選択図】図３A heat sink core structure is provided which has improved heat transfer performance in the thickness direction of the heat sink and improved heat exchange performance by promoting stirring of a coolant.
A plurality of vertical members 1a and 2a are provided in parallel in the width direction of a first plate 1 and a second plate 2, and oblique members 1b are provided between adjacent vertical members 1a and between vertical members 2a. The slanting member 2b is integrally formed. Then, the first plate 1 and the second plate 2 are stacked, the vertical members 1a and 2a are aligned and overlapped, and the oblique member 1b of the first plate 1 and the oblique member 2b of the second plate 2 are , Spaced apart from each other in the flow direction and reversed in direction.
[Selection] Figure 3

Description

本発明は、半導体チップ等のパワーデバイスを冷却するヒートシンクに関し、より詳しくはその内部に挿入されるコアに関する。   The present invention relates to a heat sink for cooling a power device such as a semiconductor chip, and more particularly to a core inserted therein.

従来のパワーモジュール用ヒートシンクは、内部に冷却液を流通させる偏平な矩形断面をなすケーシングの外面にパワーモジュールを搭載し、内部の冷媒流路にフィンを固定したものである。
一例として、下記特許文献１に示すものは、ケーシング内の冷媒流路内に薄肉のコルゲートフィンを配置し、そのコルゲートフィンに無数のルーバを配置したものである。
また、下記特許文献２に記載のものは、ケーシング内に平面網状プレートを多数積層したものであり、隣接するプレートの網目が互いに位置ずれしたものである。 A conventional heat sink for a power module has a power module mounted on the outer surface of a casing having a flat rectangular cross section through which a coolant flows, and fins are fixed to an internal refrigerant flow path.
As an example, what is shown in Patent Document 1 below is one in which thin corrugated fins are arranged in a refrigerant flow path in a casing, and innumerable louvers are arranged in the corrugated fins.
In addition, the one described in Patent Document 2 below is obtained by laminating a large number of planar mesh plates in a casing, and the meshes of adjacent plates are displaced from each other.

特開２００７−５６７３号公報JP 2007-5673 A 特許第２８６２２１３号公報Japanese Patent No. 2862213

前者のヒートシンクは、比較的薄肉のコルゲートフィンをインナーフィンとして内装するため、ケーシングの厚み方向における熱伝導が悪い欠点がある。ケーシング外面のパワーモジュールの熱は、ケーシングから波形フィンの立ち上がり面及び立ち下がり面を介して冷却液に伝達されるが、そのフィン自体の厚みが薄いため伝熱が良好に行われ難い欠点がある。   The former heat sink has a disadvantage that heat conduction in the thickness direction of the casing is poor because a relatively thin corrugated fin is used as an inner fin. The heat of the power module on the outer surface of the casing is transferred from the casing to the coolant through the rising and falling surfaces of the corrugated fins, but the fin itself has a small thickness, which makes it difficult to transfer heat well. .

これに対し、後者のヒートシンクは多孔の金属板を重ね合わせたものの、その重ね合わせ部が比較的小さく、伝熱性が充分でない。また、積層されたプレートの交差部が多く、内部を流通する冷却液の流通抵抗が過大になる欠点がある。
そこで本発明は、係る欠点を取り除くことを課題とする。 On the other hand, although the latter heat sink is an overlap of porous metal plates, the overlap portion is relatively small and the heat transfer property is not sufficient. In addition, there are many crossed portions of the stacked plates, and there is a drawback that the flow resistance of the coolant flowing inside is excessive.
Then, this invention makes it a subject to remove the fault which concerns.

請求項１に記載の本発明は、内部に冷却液が流通すると共に、外面に被冷却用の素子が取り付けられるケーシング(7) を有し、そのケーシング(7)内に、その内面に接触して挿入されるヒートシンク用コアにおいて、
それぞれ金属板の打ち抜き成形による平板状の第１プレート(1)と、第２プレート(2)との積層体からなり、
両プレート(1)(2)には、冷却液の流れ方向に直交する方向に互いに平行に離間して並列されると共に、それぞれ冷却液の流れ方向に位置された細長い多数の縦部材(1a)(2a)と、隣り合う縦部材(1a)(2a)間を斜めに接続する斜め部材(1b)(2b)とが一体に形成され、
両プレート(1)(2)は、それぞれの各縦部材(1a)(2a)が整合して重なり、夫々の斜め部材(1b)(2b)は前記流れ方向に互いに離間して配置されると共に、その向きが互いに逆向きに配置されたことを特徴とするヒートシンク用コア構造である。 The present invention according to claim 1 has a casing (7) in which a coolant is circulated inside and an element to be cooled is attached to the outer surface, and the inner surface is in contact with the inner surface of the casing (7). In the heat sink core inserted
Each consists of a laminate of flat plate-like first plate (1) and second plate (2) by punching metal plate,
The two plates (1) and (2) are arranged in parallel and spaced apart from each other in a direction orthogonal to the flow direction of the coolant, and a plurality of elongated vertical members (1a) positioned in the flow direction of the coolant, respectively. (2a) and the oblique members (1b) (2b) that obliquely connect the adjacent vertical members (1a) (2a) are integrally formed,
The two plates (1) and (2) are overlapped in alignment with the respective vertical members (1a) and (2a), and the oblique members (1b) and (2b) are arranged apart from each other in the flow direction. The heat sink core structure is characterized in that the directions are arranged in opposite directions.

請求項２に記載の本発明は、請求項１において、
積層方向に隣り合う第１プレート(1)の縦部材(1a)と、第２プレート(2)の縦部材(2a)との間のみにスペーサ(3)が介装されたヒートシンク用コア構造である。
請求項３に記載の本発明は、請求項１または請求項２において、
前記第１プレート(1)および第２プレート(2)の各縦部材(1a)(2a)が平面的に波形に曲折されてなるヒートシンク用コア構造である。 The present invention according to claim 2 is the method according to claim 1,
A heat sink core structure in which a spacer (3) is interposed only between the vertical member (1a) of the first plate (1) and the vertical member (2a) of the second plate (2) adjacent to each other in the stacking direction. is there.
According to a third aspect of the present invention, in the first or second aspect,
It is a heat sink core structure in which the vertical members (1a) and (2a) of the first plate (1) and the second plate (2) are bent into a waveform in a plane.

請求項４に記載の本発明は、請求項１において、
所定長さのコア(4)が、流体の流通方向に断続的に配置されたヒートシンク用コア構造である。
請求項５に記載の本発明は、請求項１または請求項３において、
各プレート(1)(2)の各縦部材(1a)(2a)の側面に突起(5)を一体に設けたヒートシンク用コア構造である。
請求項６に記載の本発明は、請求項１〜請求項５のいずれかにおいて、
各プレート(1)(2)どうしが、積層方向にろう付け等の手段により接合されたヒートシンク用コア構造である。 The present invention according to claim 4 provides the method according to claim 1,
This is a heat sink core structure in which the core (4) having a predetermined length is intermittently arranged in the fluid flow direction.
The present invention according to claim 5 provides the method according to claim 1 or claim 3,
This is a heat sink core structure in which protrusions (5) are integrally provided on the side surfaces of the vertical members (1a) and (2a) of the plates (1) and (2).
A sixth aspect of the present invention provides the method according to any one of the first to fifth aspects,
Each of the plates (1) and (2) has a heat sink core structure joined in the stacking direction by means such as brazing.

本発明のヒートシンク用コアは、平板状の第１プレート１と第２プレート２との積層体からなり、多数の夫々の縦部材1a，縦部材2aは互いに整合して重なり合うため、積層方向の熱伝達がよく、結果、ケーシング７との熱伝達が良好に行われる。そして、第１プレート１の斜め部材1b，第２プレート２の斜め部材2bは、互いに流れ方向に離間して配置されると共に、その向きが互いに逆向きに対称に配置されているから、各縦部材間の流路６を流通する冷却液11は積層方向に規則的に蛇行すると共に、流路６の幅方向に規則的に蛇行し、結果として冷却液11は各流路６に沿って螺旋状に回転しながら流通し、熱交換を促進することができる。   The heat sink core of the present invention is composed of a laminated body of a flat plate-like first plate 1 and second plate 2, and a large number of the vertical members 1a and 2a are aligned and overlapped with each other. As a result, heat transfer with the casing 7 is favorably performed. The oblique member 1b of the first plate 1 and the oblique member 2b of the second plate 2 are arranged so as to be separated from each other in the flow direction, and their orientations are arranged symmetrically opposite to each other. The coolant 11 flowing through the channel 6 between the members regularly meanders in the stacking direction and regularly meanders in the width direction of the channel 6, and as a result, the coolant 11 spirals along each channel 6. It can distribute | circulate, rotating, and can promote heat exchange.

さらに、各斜め部材1b，斜め部材2bは夫々冷却液11の流通方向に対して斜めに配置されているため、それらの存在する各横断面は流路の入口側から出口側に向けて、図１１の如く山形に、徐々に減少し次いで徐々に増加し、流路抵抗の急激な増加を防止して、冷却液の流通に伴う圧力損失を比較的低い値に維持できる。
また、斜め部材1b，斜め部材2bは流れ方向に互いに離間しているため、各斜め部材の全外周において冷却液11との熱交換が行われる。 Further, since each of the oblique members 1b and the oblique members 2b are disposed obliquely with respect to the flow direction of the coolant 11, the respective cross sections thereof exist from the inlet side to the outlet side of the flow path. As shown in FIG. 11, it gradually decreases in a mountain shape and then gradually increases, preventing a rapid increase in flow path resistance and maintaining the pressure loss associated with the flow of the coolant at a relatively low value.
Further, since the oblique member 1b and the oblique member 2b are separated from each other in the flow direction, heat exchange with the coolant 11 is performed on the entire outer periphery of each oblique member.

上記構成において、請求項２に記載のように第１プレート１の縦部材1aと第２プレート２の縦部材2aとの間のみにスペーサ３を介装した場合には、コア内部の冷却液11の圧力損失をさらに減少し得る。
上記構成において、請求項３に記載のように第１プレート１及び第２プレート２の各縦部材1a，縦部材2aを平面的に波形に曲折した場合には、伝熱面積が増加すると共に、各流路６を流通する冷却液11を幅方向にさらに蛇行させることにより、冷却液と伝熱部分の接触時間および接触距離が長くなり、熱交換性能を向上し得る。 In the above configuration, when the spacer 3 is interposed only between the vertical member 1a of the first plate 1 and the vertical member 2a of the second plate 2 as described in claim 2, the coolant 11 inside the core 11 The pressure loss can be further reduced.
In the above configuration, when each of the vertical members 1a and 2a of the first plate 1 and the second plate 2 is bent in a planar shape as described in claim 3, the heat transfer area increases, By further meandering the cooling liquid 11 flowing through each flow path 6 in the width direction, the contact time and the contact distance between the cooling liquid and the heat transfer portion are increased, and the heat exchange performance can be improved.

上記構成において、請求項４に記載のように所定長さのコア４を流体の流通方向に断続的に配置した場合には、必要に応じて適宜容量のヒートシンクを、コアの数の調整により容易に製造することができる。
上記構成において、請求項５に記載のように第１プレート１，第２プレート２の縦部材1a，2aの側面に突起５を一体に設けた場合には、伝熱面積の増加と、各流路６内の冷却液11の攪拌とにより熱交換を促進することができる。
上記構成において、請求項６に記載のように第１プレート１，第２プレート２どうしを積層方向にろう付け等の手段により接合した場合には、その積層方向の熱伝達をさらに向上し得る。 In the above configuration, when the core 4 having a predetermined length is intermittently arranged in the fluid flow direction as described in claim 4, an appropriate capacity heat sink can be easily adjusted by adjusting the number of cores as required. Can be manufactured.
In the above configuration, when the protrusions 5 are integrally provided on the side surfaces of the vertical members 1a and 2a of the first plate 1 and the second plate 2 as described in claim 5, the heat transfer area is increased and each flow is increased. Heat exchange can be promoted by stirring the coolant 11 in the passage 6.
In the above configuration, when the first plate 1 and the second plate 2 are joined to each other in the stacking direction by means such as brazing as described in claim 6, heat transfer in the stacking direction can be further improved.

次に、図面に基づいて本発明の実施の形態につき説明する。
図１は本発明のコア４を構成する第１プレート１の平面図、図２は同第２プレート２の平面図、図３は同コア４の平面図、図４はその斜視図、図５は一対の同コア４を内装したヒートシンクの分解斜視図、図６は同横断面図である。
このコア４は、第１プレート１と第２プレート２とを交互に積層したものである。第１プレート１，第２プレート２は夫々アルミニューム等の金属板の打ち抜き加工により形成されたものであり、両プレートには幅方向に多数の直線状の縦部材1a，2aが定間隔に並列されている。そして隣り合う縦部材1a間及び2a間を、斜め部材1b，2bによって一体に接続する。 Next, embodiments of the present invention will be described with reference to the drawings.
1 is a plan view of the first plate 1 constituting the core 4 of the present invention, FIG. 2 is a plan view of the second plate 2, FIG. 3 is a plan view of the core 4, FIG. 4 is a perspective view thereof, FIG. Is an exploded perspective view of a heat sink having a pair of the same cores 4, and FIG. 6 is a cross-sectional view thereof.
The core 4 is formed by alternately laminating the first plate 1 and the second plate 2. The first plate 1 and the second plate 2 are formed by punching a metal plate such as aluminum, and a large number of straight vertical members 1a and 2a are arranged in parallel at regular intervals in the width direction. Has been. The adjacent vertical members 1a and 2a are integrally connected by the oblique members 1b and 2b.

第１プレート１，第２プレート２が積層されたとき、図３に示す如く、第１プレート１の縦部材1aと第２プレート２の縦部材2aとは整合して重なり合い、第１プレート１の斜め部材1bと第２プレート２の斜め部材2bとは、その長手方向に互いに離間して配置されると共に、第１プレート１の斜め部材1bの向きと、第２プレート２の斜め部材2bの向きは逆向きの対称（傾斜角度が、縦部材に対して、一方をθとすれば他方は−θ）に形成されている。
なお、第２プレート２の斜め部材2bの位置は、第１プレート１の長手方向に隣り合う斜め部材1bの中間に存在する。また、この例では、両プレート１，２の厚みを同一としたが、それが異なったものでもよい。
このように第１プレート１，第２プレート２が積層されたコア４は、一例として図５及び図６に示す如く、ケーシング７の内部に収納される。この例では、ケーシング７は皿状のケーシング本体7aと平板状のケーシング蓋7bとからなる。ケーシング本体7aは外周及び中間部が立ち上げられ、それらの間に一対の溝部10が形成され、一対の溝部10の端部間は連通し、そこに両コア４共通のタンク部10aを設けている。そしてケーシング蓋7bには、その長手方向両端に冷却液の出入口９が形成され、それが前記タンク部10aに連通している。 When the first plate 1 and the second plate 2 are laminated, the vertical member 1a of the first plate 1 and the vertical member 2a of the second plate 2 are aligned and overlapped as shown in FIG. The oblique member 1b and the oblique member 2b of the second plate 2 are arranged apart from each other in the longitudinal direction, and the orientation of the oblique member 1b of the first plate 1 and the orientation of the oblique member 2b of the second plate 2 Are symmetrical in the opposite direction (inclination angle with respect to the longitudinal member, if one is θ, the other is −θ).
The position of the oblique member 2b of the second plate 2 exists in the middle of the oblique member 1b adjacent in the longitudinal direction of the first plate 1. In this example, the thicknesses of both plates 1 and 2 are the same, but they may be different.
The core 4 in which the first plate 1 and the second plate 2 are stacked in this way is housed in the casing 7 as shown in FIGS. 5 and 6 as an example. In this example, the casing 7 is composed of a dish-shaped casing body 7a and a plate-shaped casing lid 7b. The casing body 7a has an outer periphery and an intermediate portion raised, a pair of groove portions 10 are formed between them, and the ends of the pair of groove portions 10 communicate with each other, and a tank portion 10a common to both cores 4 is provided there. Yes. The casing lid 7b is formed with a coolant inlet / outlet port 9 at both longitudinal ends thereof, and communicates with the tank portion 10a.

コア４は、その積層方向である上下両面がケーシング本体7a，ケーシング蓋7bに接触し、全体が一体的にろう付け固定されている。即ち、第１プレート１と第２プレート２との間及びそれらとケーシング７内面との間が一体にろう付け固定される。そして、ケーシング７の一方の出入口９から冷却液が内部に導かれ、それが一対のコア４を流通して他方の出入口９から流出する。
なお、ケーシング７の外面にはパワーモジュール等の被冷却用の素子が取り付けられ、その発熱がコア４を介して冷却液に吸収させるものである。このとき冷却液は、図３，図４においてその長手方向に流通する。その冷却液11は、各第１プレート１，第２プレート２の隣り合う縦部材1aどうし及び、2aどうしの間の流路６を流通する。 As for the core 4, the upper and lower surfaces which are the lamination directions contact the casing main body 7a and the casing lid 7b, and the whole is integrally brazed and fixed. That is, between the first plate 1 and the second plate 2 and between them and the inner surface of the casing 7 are integrally brazed and fixed. Then, the coolant is introduced into one of the inlets and outlets 9 of the casing 7, and flows through the pair of cores 4 and flows out of the other inlet / outlet 9.
An element to be cooled such as a power module is attached to the outer surface of the casing 7, and the generated heat is absorbed by the coolant through the core 4. At this time, the coolant flows in the longitudinal direction in FIGS. The cooling liquid 11 flows through the flow path 6 between the adjacent vertical members 1a and 2a of the first plate 1 and the second plate 2.

その冷却液11の流通の状態を図７及び図８に示す。図７はその要部縦断面図であり、図８はその要部平面図である。
図８において、隣り合う縦部材1aどうし及び縦部材2aどうしの間を流通する冷却液11は、斜め部材1b，2bの位置において、それらの存在により、図７の如く上下方向に蛇行すると共に、図８の如く平面方向にも蛇行する。これは斜め部材1b，2bが流路６に対して斜めに逆対称に配置されているためである。その結果、冷却液11は平面的に蛇行すると共に上下方向に蛇行し、結果として流路６内を螺旋状に流通するものである。 The state of circulation of the coolant 11 is shown in FIGS. FIG. 7 is a longitudinal sectional view of the main part, and FIG. 8 is a plan view of the main part.
In FIG. 8, the coolant 11 flowing between the adjacent vertical members 1a and 2a is meandering in the vertical direction as shown in FIG. 7 due to their presence at the positions of the diagonal members 1b and 2b. It also meanders in the plane direction as shown in FIG. This is because the oblique members 1b and 2b are disposed in an obliquely antisymmetric manner with respect to the flow path 6. As a result, the cooling liquid 11 meanders in a plane and meanders in the vertical direction, and as a result, it circulates in the flow path 6 in a spiral shape.

このとき流路６の横断面積は、斜め部材1b，斜め部材2bの位置において、その上流側から中間部に次第に減少し、中間部から下流側に次第に増加する。このことを図９，図１０で示す。図９はコア４の要部平面図であり、その流路６の図９におけるＡ位置の横断面は図１０のＡであり、斜め部材1bの存在しない位置と同一であり、Ｂ断面，Ｃ断面，Ｄ断面と次第にその流路断面積が斜め部材1bの存在により減少する。そして断面Ｅ〜Ｇでは最小となり、ＨにおいてＤと同一断面となり、ＩにおいてＣと同一断面であり、ＪにおいてＢと同一であり、ＫにおいてＡと同一となる。   At this time, the cross-sectional area of the flow path 6 gradually decreases from the upstream side to the intermediate portion and gradually increases from the intermediate portion to the downstream side at the positions of the oblique member 1b and the oblique member 2b. This is shown in FIGS. 9 is a plan view of the main part of the core 4. The cross section at the position A in FIG. 9 of the flow path 6 is A in FIG. 10, which is the same as the position where the oblique member 1b does not exist, and the cross section B, C The cross section, the D cross section, and the flow path cross sectional area gradually decrease due to the presence of the oblique member 1b. It is the smallest in the sections E to G, the same section as D in H, the same section as C in I, the same section as B in J, and the same section as A in K.

これを流路に沿って表現すると、図１１の通りとなる。同図において、ｍはコア４の要部平面図であり、ｎはその流路断面積の変化を％で表したものである。これは、斜め部材1b、2bの存在しない位置における流路６の横断面を１００％とし、それらが存在する場所での各流路断面の変化を表したものである。同図から明らかなように斜め部材1b，2bにおいて、その流路断面は下流側に次第に減少し、中間で一定となった後に次第に増加する。このことは流路６の急激な増減を避け、徐々の減少及び徐々の増加によって冷却液11の流通に伴う圧力損失を可及的に小さくしつつ、その攪拌効果を増大させるものである。   This can be expressed along the flow path as shown in FIG. In the figure, m is a plan view of the main part of the core 4, and n is a change in flow channel cross-sectional area expressed in%. This represents a change in the cross section of each flow path at the location where the cross section of the flow path 6 at a position where the oblique members 1b and 2b do not exist is 100%. As is clear from the figure, in the slant members 1b and 2b, the cross section of the flow path gradually decreases to the downstream side and gradually increases after becoming constant in the middle. This avoids a sudden increase / decrease in the flow path 6 and increases the stirring effect while minimizing the pressure loss associated with the circulation of the coolant 11 by gradually decreasing and increasing gradually.

次に、図１２〜図１４は本発明の第２の実施の形態のコアを示し、この例が前記第１の実施の形態と異なる点は、図１２に示す如く第１プレート１と第２プレート２との間にスペーサ３を介装したものである。
このスペーサ３は、第１プレート１の縦部材1aと第２プレート２の縦部材2aの位置のみに介装され、それらが一体的にろう付け固定されたものである。このスペーサ３の存在により、冷却液11の流通に伴う流路抵抗をさらに減少させるものである。このときの流路断面の変化割合は、図１４に示す如く、前記第１実施例のそれより少ない。即ち、流路変化の割合が小となっている。 Next, FIGS. 12 to 14 show a core according to a second embodiment of the present invention. This example is different from the first embodiment in that the first plate 1 and the second plate 1 are different from the first embodiment as shown in FIG. A spacer 3 is interposed between the plate 2 and the plate 2.
The spacer 3 is interposed only at the position of the vertical member 1a of the first plate 1 and the vertical member 2a of the second plate 2, and is integrally brazed and fixed. The presence of the spacer 3 further reduces the channel resistance associated with the circulation of the coolant 11. At this time, the change rate of the flow path cross section is smaller than that of the first embodiment as shown in FIG. That is, the flow rate change rate is small.

次に、図１５〜図１７は本発明の第３の実施の形態を示し、この例が前記第１の実施の形態と異なる点は、第１プレート１，第２プレート２の各縦部材1a，縦部材2aの側面に夫々突起５を一体に突出したものである。
そして、図１７に示す如く、第１プレート１，第２プレート２を積層したとき、各プレート１，２の各突起５が整合するものである。その結果、各突起５が厚み方向に連続し凸条を形成する。その結果、流路内においてその凸状に基づいて冷却液11はその位置で蛇行し攪拌される。それによって、熱交換性能が向上する。 Next, FIGS. 15 to 17 show a third embodiment of the present invention. This example is different from the first embodiment in that each vertical member 1a of the first plate 1 and the second plate 2 is shown. The protrusions 5 are integrally projected on the side surfaces of the vertical member 2a.
And as shown in FIG. 17, when the 1st plate 1 and the 2nd plate 2 are laminated | stacked, each protrusion 5 of each plate 1 and 2 aligns. As a result, each protrusion 5 is continuous in the thickness direction to form a ridge. As a result, the cooling liquid 11 meanders and stirs at that position based on the convex shape in the flow path. Thereby, the heat exchange performance is improved.

次に、図１８は本発明の第４の実施の形態を示す平面図であり、この例は所定長さのコア４を断続的に直列方向に配置したものである。このようにコア４を所定長さのブロックとすることにより、その接続数の増減によって適宜容量のヒートシンクを容易に製造することができる。   Next, FIG. 18 is a plan view showing a fourth embodiment of the present invention. In this example, cores 4 having a predetermined length are intermittently arranged in a series direction. Thus, by making the core 4 into a block having a predetermined length, a heat sink having an appropriate capacity can be easily manufactured by increasing or decreasing the number of connections.

次に、図１９〜図２２は本発明の第５の実施の形態を示し、図１９はその第１プレート１の平面図、図２０は第２プレート２の平面図、図２１はその組み合わせ状態を示すコア４の平面図、図２２は同コア４の斜視略図である。
このコア４を構成する第１プレート１，第２プレート２は、夫々の縦部材1a，2aが平面視、定ピッチで波形に曲折されている。そして隣り合う縦部材1aどうし及び縦部材2aどうしを、斜め部材1b，斜め部材2bによって一体に接続したものである。この例でも、第１プレート１，第２プレート２の縦部材1a，縦部材2aどうしは図２１の如く互いに整合する。そして第１プレート１の斜め部材1bと、第２プレート２の斜め部材2bは流路６の流れ方向に互いに離間して配置されている。この例では、縦部材1a，縦部材2aが蛇行状に形成されているため、その蛇行された流路６に対し斜め部材1b，2bは、その蛇行流れに対しそれぞれ傾斜し且つ、両斜め部材1b，2bはその蛇行流れに対して互いに向きが逆向きに形成されている。 19 to 22 show a fifth embodiment of the present invention. FIG. 19 is a plan view of the first plate 1, FIG. 20 is a plan view of the second plate 2, and FIG. FIG. 22 is a schematic perspective view of the core 4.
In the first plate 1 and the second plate 2 constituting the core 4, the longitudinal members 1a and 2a are bent into a waveform at a constant pitch in plan view. Adjacent vertical members 1a and vertical members 2a are integrally connected by an oblique member 1b and an oblique member 2b. Also in this example, the vertical members 1a and 2a of the first plate 1 and the second plate 2 are aligned with each other as shown in FIG. The oblique member 1b of the first plate 1 and the oblique member 2b of the second plate 2 are arranged away from each other in the flow direction of the flow path 6. In this example, since the vertical member 1a and the vertical member 2a are formed in a meandering shape, the oblique members 1b and 2b are inclined with respect to the meandering flow path 6 and both the oblique members. 1b and 2b are formed in opposite directions with respect to the meandering flow.

次に、図２３は図６のヒートシンクの変形例であり、この例はコアの長手方向の中間におけるヒートシンクの横断面である。この例では、ケーシング本体7a，ケーシング蓋7bが平板状に形成されたものを用いている。そして冷却水の流通方向の一端及び他端に、図示しない冷却液の導出入用ヘッダをもうけるものである。   Next, FIG. 23 is a modification of the heat sink of FIG. 6, and this example is a cross section of the heat sink in the middle in the longitudinal direction of the core. In this example, the casing body 7a and the casing lid 7b are formed in a flat plate shape. Then, a cooling liquid lead-in / out header (not shown) is provided at one end and the other end in the flow direction of the cooling water.

本発明のコア４を構成する第１プレート１の平面図。The top view of the 1st plate 1 which comprises the core 4 of this invention. 同第２プレート２の平面図。The top view of the 2nd plate 2. FIG. 同コア４の平面図。The top view of the same core 4. FIG. 同コア４の斜視略図。The perspective schematic diagram of the same core 4. FIG.

同コア４を有するヒートシンクの分解斜視図。The disassembled perspective view of the heat sink which has the same core 4. FIG. 同ヒートシンクの横断面略図。The cross-sectional schematic of the heat sink. 同ヒートシンク内における冷却液11の流れ状態を示す縦断面説明図。FIG. 3 is a longitudinal sectional explanatory view showing a flow state of the cooling liquid 11 in the heat sink. 同流れ状態の平面的説明図。Plane explanatory drawing of the same flow state.

同コア４の流路６の要部拡大平面図。The principal part enlarged plan view of the flow path 6 of the same core 4. FIG. 図９のＡ〜Ｋにおける各横断面の減少割合を示す説明図。Explanatory drawing which shows the decreasing rate of each cross section in AK of FIG. 同コア４の斜め部材1b，斜め部材2bの位置と減少割合との関係を％で示した説明図。Explanatory drawing which showed the relationship between the position of the diagonal member 1b of the same core 4, the diagonal member 2b, and the decreasing rate with%. 本発明の第２の実施の形態を示す横断面説明図。Cross-sectional explanatory drawing which shows the 2nd Embodiment of this invention.

同平面図。FIG. 同実施例の各流路６の斜め部材1b，斜め部材2bにおける流路断面の減少割合を示す説明図。Explanatory drawing which shows the decreasing rate of the flow-path cross section in the diagonal member 1b of each flow path 6 of the Example, and the diagonal member 2b. 本発明の第３の実施の形態を示す第１プレート１の平面図。The top view of the 1st plate 1 which shows the 3rd Embodiment of this invention. 同第２プレート２の平面図。The top view of the 2nd plate 2. FIG.

同コア４の平面図。The top view of the same core 4. FIG. 本発明の第４の実施の形態を示す平面的説明図。Plane | planar explanatory drawing which shows the 4th Embodiment of this invention. 本発明の第５の実施の形態を示す第１プレート１の平面図。The top view of the 1st plate 1 which shows the 5th Embodiment of this invention. 同第２プレート２の平面図。The top view of the 2nd plate 2. FIG.

同コア４の平面図。The top view of the same core 4. FIG. 同コア４の斜視略図。The perspective schematic diagram of the same core 4. FIG. 本発明の第６のヒートシンクの横断面略図。The cross-sectional schematic of the 6th heat sink of this invention.

符号の説明Explanation of symbols

１ 第１プレート
1a 縦部材
1b 斜め部材
２ 第２プレート
2a 縦部材
2b 斜め部材 1 First plate
1a Longitudinal member
1b Diagonal member 2 Second plate
2a Longitudinal member
2b Diagonal member

３ スペーサ
４ コア
５ 突起
６ 流路
７ ケーシング
7a ケーシング本体
7b ケーシング蓋 3 Spacer 4 Core 5 Protrusion 6 Flow path 7 Casing
7a Casing body
7b Casing lid

９ 出入口
10 溝部
10a タンク部
11 冷却液 9 Entrance
10 Groove
10a Tank part
11 Coolant

Claims (6)

内部に冷却液が流通すると共に、外面に被冷却用の素子が取り付けられるケーシング(7) を有し、そのケーシング(7)内に、その内面に接触して挿入されるヒートシンク用コアにおいて、
それぞれ金属板の打ち抜き成形による平板状の第１プレート(1)と、第２プレート(2)との積層体からなり、
両プレート(1)(2)には、冷却液の流れ方向に直交する方向に互いに平行に離間して並列されると共に、それぞれ冷却液の流れ方向に位置された細長い多数の縦部材(1a)(2a)と、隣り合う縦部材(1a)(2a)間を斜めに接続する斜め部材(1b)(2b)とが一体に形成され、
両プレート(1)(2)は、それぞれの各縦部材(1a)(2a)が整合して重なり、夫々の斜め部材(1b)(2b)は前記流れ方向に互いに離間して配置されると共に、その向きが互いに逆向きに配置されたことを特徴とするヒートシンク用コア構造。 In the heat sink core inserted into the casing (7) in contact with the inner surface, the casing (7) has a cooling liquid flowing inside and an element to be cooled is attached to the outer surface.
Each consists of a laminate of flat plate-like first plate (1) and second plate (2) by punching metal plate,
The two plates (1) and (2) are arranged in parallel and spaced apart from each other in a direction orthogonal to the flow direction of the coolant, and a plurality of elongated vertical members (1a) positioned in the flow direction of the coolant, respectively. (2a) and the oblique members (1b) (2b) that obliquely connect the adjacent vertical members (1a) (2a) are integrally formed,
The two plates (1) and (2) are overlapped in alignment with the respective vertical members (1a) and (2a), and the oblique members (1b) and (2b) are arranged apart from each other in the flow direction. The heat sink core structure is characterized in that the directions are arranged in opposite directions. 請求項１において、
積層方向に隣り合う第１プレート(1)の縦部材(1a)と、第２プレート(2)の縦部材(2a)との間のみにスペーサ(3)が介装されたヒートシンク用コア構造。 In claim 1,
A heat sink core structure in which a spacer (3) is interposed only between the vertical member (1a) of the first plate (1) and the vertical member (2a) of the second plate (2) adjacent to each other in the stacking direction. 請求項１または請求項２において、
前記第１プレート(1)および第２プレート(2)の各縦部材(1a)(2a)が平面的に波形に曲折されてなるヒートシンク用コア構造。 In claim 1 or claim 2,
A heat sink core structure in which the longitudinal members (1a) and (2a) of the first plate (1) and the second plate (2) are bent into a waveform in a planar manner. 請求項１において、
所定長さのコア(4)が、流体の流通方向に断続的に配置されたヒートシンク用コア構造。 In claim 1,
A heat sink core structure in which a predetermined length of the core (4) is intermittently arranged in the fluid flow direction. 請求項１または請求項３において、
各プレート(1)(2)の各縦部材(1a)(2a)の側面に突起(5)を一体に設けたヒートシンク用コア構造。 In claim 1 or claim 3,
A heat sink core structure in which a protrusion (5) is integrally provided on the side surface of each vertical member (1a) (2a) of each plate (1) (2). 請求項１〜請求項５のいずれかにおいて、
各プレート(1)(2)どうしが、積層方向にろう付け等の手段により接合されたヒートシンク用コア構造。 In any one of Claims 1-5,
A heat sink core structure in which the plates (1) and (2) are joined together by means such as brazing in the stacking direction.
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US11935815B2 (en) 2019-02-08 2024-03-19 Uacj Corporation Heat sink and heat exchanger
WO2022248427A1 (en) * 2021-05-27 2022-12-01 Valeo Eautomotive Germany Gmbh Cooling structure, power module comprising such a cooling structure, electrical power converter, such as an inverter, comprising such a power module
DE112021008434T5 (en) 2021-11-04 2024-08-14 Mitsubishi Electric Corporation HEAT SINK AND METHOD FOR PRODUCING A HEAT SINK

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