200819701 (1) 九、發明說明 【發明所屬之技術領域】 本發明涉及一種散熱效率良好的熱交換器，尤 一種對在散熱翼片間流動的冷卻用空氣的流動進行 提高與翼片間的熱交換的、由底板（base plate ) 翼片構成的熱交換器。 【先前技術】 由於CPU、元件等的發熱量、發熱密度的增大 一種散熱效率良好的高性能的熱交換器。目前，一 由製造成本低廉的鋁的擠壓型材構成的熱交換器。 型材構成的熱交換器，由於底板和散熱翼片形成一 此容易製造。另外，底板和散熱翼片分開製造，在 一側的面上接合散熱翼片來製造熱交換器。 圖6是表示現有的熱交換器的立體圖。如圖6 現有的熱交換器1 00具有：一側的面上熱連接發熱 底板1 0 2、和在底板的另一側的面上熱連接的多個 熱翼片1〇3。 現有的熱交換器1〇〇，從一側的端部在底板的 向上由風扇等如符號108所示吹冷卻用空氣，將從 件經由底板向板狀散熱翼片傳導的熱向大氣中散熱 底板的長度方向熱連接有多個發熱零件的情況下， 這些多個發熱零件的熱散發’大量的冷卻用空氣從 端部被吹向板狀散熱翼片間（參照曰本特開平7_ 其涉及 減速來 和散熱 ，需求 直利用 由擠壓 體，因 底板的 所示， 零件的 板狀散 長度方 發熱零 。在沿 爲了使 一側的 -15160 200819701 (2) 號公報）。 在上述的在底板的一側的面上熱連接有多個板狀散熱 翼片的熱交換器中，一般的，被供給的冷卻用空氣的量由 各裝置決定。如果板狀散熱翼片的長度長，板狀散熱翼片 的間隔小，則會產生冷空氣碰到前面的翼片但冷空氣不能 碰到裏面的翼片的狀態。另一方面，如果使板狀散熱翼片 的間隔變大，期待冷卻效率，使大量的冷卻空氣流在高速 φ 下吹向翼片，由於空氣只通過翼片間的中央部，產生熱交 換進行得不充分的肤態。因此，在現有的冷卻熱交換器的 方法中，具有如下問題點，即，無法有效冷卻遍及縱深而 配置的多個發熱零件的熱、尤其是下風的發熱零件的熱。 【發明內容】 因此，本發明的目的在於提供一種能夠有效冷卻遍及 縱深而配置的多個發熱零件的散熱效率良好的熱交換器。 # 發明者爲了解決上述現有的問題點進行反復的硏究。 其結果確定了 ：若降低在板狀翼片間流動的冷卻空氣的流 速，使溫度邊界層（即，在空氣流通過翼片間時，翼片的 熱被傳遞，空氣流的一部分的溫度上升，在與不受翼片的 熱影響的空氣流的部分之間產生邊界。將此時的邊界層稱 爲溫度邊界層）重合，則能使熱交換器的板狀翼片的表面 的溫度接近於在翼片的出口側的溫度。 即，確定了 ：即使向板狀翼片間儘量地吹入高速的冷 卻空氣流，冷卻空氣流的相當一部分也與熱交換無關而只 -5- 200819701 (3) 是簡單地通過板狀翼片間，爲了提高散熱效率，必須對板 狀翼片的間隔、板狀翼片的長度、在板狀翼片間流動的冷 卻空氣的流速的關係進行適當的要求。本發明，基於上述 硏究成果而提出。 本發明的熱交換器的第1方式是如下的熱交換器，其 具有：底板部’其在一側的面上熱連接有至少1個發熱零 件；至少1個的翼片部，其由沿著上述底板部的另一側的 • 面的長度方向以規定的角度並列配置、並與底板熱連接的 多個翼片構成；入口部，其向上述至少1個的翼片部分別 送入冷卻用空氣；擋板部及隔板部，其引導上述冷卻用空 氣的流動，使得在上述至少1個的翼片部的各個之中使冷 卻用空氣在各翼片間減速而大致均勻地流動；以及排出 口，其排出冷卻用空氣。 本發明的熱交換器的第2方式是如下的熱交換器，其 具有：由多個翼片構成的至少1個的翼片部；入口部，其 • 向上述至少1個的翼片部分別送入冷卻用空氣；擋板部及 隔板部，其引導上述冷卻用空氣的流動，使得在上述至少 1個的翼片部的各個之中使冷卻用空氣在各翼片間減速而 大致均勻地流動；以及排出口，其排出冷卻用空氣。 本發明的熱交換器的第3方式是如下的熱交換器，其 具有：底板部，其熱連接有至少1個發熱零件；翼片群， 其配置有至少2個的翼片部，以形成對在翼片間流動的冷 卻用空氣的流速進行減速的構造，上述至少2個的翼片部 沿著上述底板部的長度方向以規定的角度並列配置’並由 -6- 200819701 (4) 與上述底板熱連接的多個翼片構成；入口部，其向上述至 少2個的翼片部分別送入冷卻用空氣；以及排出口，其排 出冷卻用空氣，配置上述翼片群以引導上述冷卻用空氣的 流動，使得在上述至少2個的翼片部的各個之中使冷卻用 空氣在各翼片間減速而大致均勻地流動。 ‘ 本發明的熱交換器的第4方式是如下的熱交換器，其 使對上述冷卻用空氣的流速進行減速的構造，以從上述入 φ 口部向上述排出口逐漸變窄的方式配置成八字形。 本發明的熱交換器的第5方式是如下的熱交換器，上 述翼片群，以從上述入口部向上述排出口逐漸變窄的方式 配置成八字形，在上述翼片群的上述排出口側還具有在上 述底板的長度方向上配置的另外的至少1對翼片。 本發明的熱交換器的第6方式是如下的熱交換器，上 述至少1個的翼片部由1個翼片部構成，上述隔板部被配 置在上述翼片部的兩側端部，上述擋板部被配置在最近端 # 部及最遠端部的翼片的附近。 本發明的熱交換器的第7方式是如下的熱交換器，上 述至少1個的翼片部由沿上述底板的寬度方向配置的多個 翼片部構成，上述隔板部被配置在上述翼片部之間及兩外 側端部，上述擋板部被配置在各翼片部的最近端部及最遠 端部的翼片的附近。 本發明的熱交換器的第8方式是如下的熱交換器，從 上述入口以高速送入散熱器的冷卻用空氣沿著一通路流 動，上述通路沿著上述隔板部形成在多個翼片的一側的端 200819701 (5) 部和上述隔板部之間，上述冷卻用空氣被上述擋板部及上 述隔板部引導而減速，在翼片間流動，沿著在多個翼片的 另一側的端部和上述隔板部之間形成的通路流動，從上述 排出口排出。 ' 本發明的熱交換器的第9方式是如下的熱交換器，對 ' 翼片間隔、翼片長度及在翼片間流動的流速進行設定，以 使傳遞了上述發熱零件的熱的上述翼片表面的溫度和在上 φ 述排出口的冷卻用空氣的溫度之差變小。 本發明的熱交換器的第1 〇方式是如下的熱交換器， 對在翼片間流動的上述冷卻用空氣進行減速，以使由在翼 片間流動的上述冷卻用空氣形成的、鄰接的翼片的各自的 溫度邊界層重疊。 本發明的熱交換器的第1 1方式是如下的熱交換器， 在設翼片間隔爲d(mm)，翼片長度爲L(m)，在翼片間流動 的流速爲 v(m/s)時，dS 9.4V57^)x3。 • 本發明的熱交換器的第1 2方式是如下的熱交換器’ 在設翼片間隔爲d(mm)，翼片長度爲L(m)，在翼片間流動 的流速爲 v(m/s)時，dg 9.4V5^x2。 本發明的熱交換器的第1 3方式是如下的熱交換器’ 在設翼片間隔爲d(mm)，翼片長度爲L(m)，在翼片間流動 的流速爲 v (m/ s )時，d g 9.4^(l/v)。 本發明的熱交換器的第14方式是如下的熱交換器’ 在上述多個翼片部的各處流動的冷卻用空氣的流量及/或 在翼片間流動的冷卻用空氣的流量不同。 -8- 200819701 (6) 本發明的熱交換器的第15方式是如下的熱交換器’ 上述熱交換器爲自然空冷的熱交換器。 本發明的熱交換器的第16方式是如下的熱交換器’ 上述熱交換器爲水冷的熱交換器。 【實施方式】 參照附圖對本發明的熱交換器進行說明。 φ 本發明的熱交換器的一個方式是如下的熱交換器，其 具有：底板部，其在一側的面上熱連接有至少1個發熱零 件；至少1個的翼片部，其由沿著上述底板部的另一側的 面的長度方向以規定的角度並列配置、並與底板熱連接的 多個翼片構成；入口部，其向上述至少1個的翼片部分別 送入冷卻用空氣；擋板部及隔板部，其引導上述冷卻用空 氣的流動，使得在上述至少1個的翼片部的各個之中使冷 卻用空氣在各翼片間減速，而大致均勻地流動；以及排出 # 口，其排出冷卻用空氣。 例如，在一個方式中，至少1個的翼片部由1個翼片 部構成，隔板部被配置在翼片部的兩側端部，擋板部被配 置在最近端部及最遠端部的板狀翼片的附近。 在以下的說明中，對於在本發明中使用的板狀翼片、 翼片部、翼片群做如下定義。即，每個板狀翼片在圖1中 是由符號3表示的翼片，所謂翼片部如圖1所示，是指多 個板狀翼片3在縱向上排列並被配置成一列的整體。所謂 翼片群是指2個翼片部配置成大致呈八字形而形成的結 -9 - 200819701 (7) 構，如圖8所示’翼片部由符號17表本’翼片群由符號 1 8表示。 圖1是說明本發明的熱交換器的局部立體圖。如圖1 所示，本發明的熱交換器具有：底板部2 ’其在背面熱連 * 接有（未圖示的）發熱零件；翼片部’其由沿著底板部的 ^ 表面的長度方向以規定的角度並列配置的多個板狀翼片3 構成；向翼片部3送入冷卻用空氣的入口部6;擋板部5 φ — 1、5 — 2及（未圖示的）隔板部，其引導冷卻用空氣的 流動，使得冷卻用空氣在翼片部的各翼片間減速，大致均 勻地流動引導；以及排出冷卻用空氣的排出口 7。在圖1 中，高速的空氣流從入口部 6 (即表面上的入口）被送 入，低速的空氣流被送入翼片間（即實際的入口）。 圖2是說明圖1所示的方式的熱交換器的俯視圖。如 圖2所示，在底板部2上，以規定的角度沿長度方向並列 配置有多個板狀翼片3。配置以規定的間隔相鄰的板狀翼 φ 片。雖然在圖1中爲了容易說明而省略了，但隔板部4被 設置在底板部2的兩側端部。在最近前的板狀翼片及最裏 面的板狀翼片上，分別設置有擋板部5 — i、5 一 2。 在熱交換器上設有送入空氣流的入口部和排出空氣流 的排出口。向熱交換器中從入口部送入高速的空氣流8。 由於在最近前的板狀翼片3上安裝有擋板部5一 1，因此利 用擋板部阻礙氣流，高速的空氣流8，沿著通過沿底板部 的長度方向並列配置的多個板狀翼片的一側的端部和隔板 部4形成的通路流動。 -10- 200819701 (8) 上述的高速的空氣流8，撃打被安裝在最遠處的板狀 翼片上的擋板部5 — 2而打亂流動，由擋板部5 — 2及隔板 部4引導，改變方向，降低速度形成低速的空氣流9，在 板狀翼片3間流動，在由沿底板部2的長度方向並列配置 ‘ 的多個板狀翼片的另一側的端部和隔板部4形成的通路處 ' 進行合流，從排出口 7被排出到熱交換器外（由符號11 表示）。 φ 參照圖4及圖5，對於本發明的熱交換器及現有的熱 交換器的散熱特性進行比較說明。 圖4是說明本發明的熱交換器的散熱特性的局部剖面 圖。圖5是說明現有的熱交換器的散熱特性的局部剖面 圖。在圖4及圖5的各自的左側部，表示由通過板狀翼片 間的冷卻空氣流形成的溫度邊界層邊界層（即，空氣流通 過翼片之間時，翼片的熱傳遞，空氣流的一部分的溫度上 升，在與不受翼片的熱的影響的空氣流的部分之間產生邊 φ 界。將這時的邊界層稱爲溫度邊界層）。在圖4及圖5的 右側部，表示翼片間隔和溫度分佈的關係。 在圖5所示的現有的熱交換器中，板狀翼片3之間的 間隔大，高速的冷卻空氣流吹過板狀翼片間。即，在溫度 邊界層1 5、1 5間，存在與熱交換無關的流動的空氣流的 空間，在翼片的表面上溫度高，與熱交換無關的流動的空 氣流的部分以保持在冷卻空氣流的方式溫度不上升。如 此，即使向板狀翼片間吹入高速的冷卻空氣流，也會產生 冷卻空氣流的相當一部分與熱交換無關，而只是簡單地通 -11 - 200819701 (9) 過板狀翼片之間的狀態（參照符號1 6 )。 如圖5的右側部所示，在板狀翼片的表面上溫度高， 在板狀翼片之間的中央部，溫度完全不上升。即，溫度差 變得非常大。因此，即使吹入高速的冷卻空氣流，翼片的 * 表面的溫度也不下降，很明顯散熱效率極差。 ^ 在圖4所示的本發明的熱交換器中，不是在高速下向 翼片吹入冷卻空氣流，如果降低在板狀翼片3之間流動的 φ 冷卻空氣的流量，使溫度邊界層 15重合，則能夠使熱交 換器的板狀翼片的表面的溫度接近於在翼片的出口側的溫 度。 即，如圖4的右側部所示，板狀翼片的表面的溫度降 低，即使在板狀翼片間的中央部也能看到溫度的上升。 即，板狀翼片的表面的溫度和翼片間的中央部的溫度的差 小，因此，翼片的表面的溫度降低，很明顯散熱效率良 好。 Φ 參照圖4進行說明的散熱效率良好的熱交換器，必須 適當地要求板狀翼片的間隔、板狀翼片的長度、在板狀翼 片間流動的冷卻空氣的流速的關係。 如在圖4中所示，從爲了使溫度邊界層相重合（即， 使溫度邊界層變得足夠厚）的條件出發，若設板狀翼片的 間隔爲d(mm)，板狀翼片的長度爲L(m)，在板狀翼片間流 動的冷卻空氣的流速爲v(m/s)，則成爲 d—2-^22 *10_6](L/v) = 9.4*10 -3 J(L/v) -12- 200819701 (10) 翼片間隔d成爲d=9A^J^/v)。 在本發明中，d S 3。更優選的是d S 9.4V57^)x 2。進一步優選的是9.4V(L/v)。本發明的本質在於適當 地要求翼片形狀、風速。爲了便於說明，利用翼片的表面 是平面的平板翼片進行了說明，但本發明的效果不僅限於 平板翼片。格子型翼片、滾花翼片（在表面上添加凹凸的 翼片）、銷翼片、在上風和下風方向上具有起伏的翼片等 也明顯地起到相同效果。 對於圖4及圖5所示的U字型的曲線進行以下的詳細 說明。 若設距離翼片入口的長度爲X、距離翼片表面的距離 爲y、空氣溫度爲T(x，t)，翼片溫度爲T0，主流的流速爲 V，熱擴散率爲a’，則空氣溫度和翼片溫度的關係可由 T(x，t)= T0*erfc(z)，z=:y/2/^/(ax/v) 表示。其中，z表示距離翼片的實質的距離。 並且，若考慮來自相鄰的翼片的影響，設翼片間隔爲 d，則成爲 T(x，t)= TO* ( erfc(z)+ erfc(z’）），z=(d-y)/2/^(ax/v)， 獲得圖4、圖5所示的11字型的曲線。 如上上述，距離翼片的實質的距離z，可以認爲是 z=y/2/V(ax/v)，因此可以將該値作爲參數進行設計。 -13- 200819701 (11) 翼片的平均溫度相對於排氣溫度的倍率，z = 3時爲 2.65倍，z = 2時爲1.79倍，z=l時爲1.12倍。 優選z < 3，更優選z < 2，最優選z < 1。 作爲典型的値，翼片間隔爲0 · 5 m m〜1 m m，翼片厚度 爲1mm〜2mm，翼片厚度被選定爲翼片間隔的2倍左右。 另外’作爲翼片長度多採用3〜20mm左右。而且， 迨只是表不一例，並非是限定本發明發揮效果的範圍。 φ 本發明的熱交換器的其他的一個方式是如下的熱交換 器’其具有··底板部，其在一側的面上熱連接有發熱零 件；多個翼片部，其由沿底板部的另一側面的長度方向以 規定的角度並列配置的多個板狀翼片構成；入口部，其向 多個翼片部分別送入冷卻用空氣；擋板部及隔板部，其引 導冷卻用空氣的流動，使得在多個翼片部的各個之中使冷 卻用空氣在各翼片間減速而大致均勻地流動；以及排出冷 卻用空氣的排出口。 # 多個翼片部沿底板的寬度方向配置，隔板部被配置在 翼片部之間及兩外側端部，擋板部與各翼片部的最近端部 及最遠端部的板狀翼片連接而配置。 圖3是說明具有多個翼片部的本發明的其他的一個方 式的熱交換器的立體圖。如圖3所示，該方式的熱交換器 10，是在底板的寬度方向上並列配置有多個參照圖1說明 了的熱交換器1，該熱交換器1被隔板部及擋板部包圍， 並且沿底板的長度方向配置有多個板狀翼片。 即，一種熱交換器具有：底板部2，其在一側的面上 -14- 200819701 (12) 熱連接有（未圖示的）發熱零件；多個翼片部，其由沿底 板部的另一側面的長度方向以規定的角度並列配置的多個 板狀翼片3構成；入口部6，其向多個翼片部分別送入冷 卻用空氣；擋板部5— 1、5— 2及隔板部4，其引導冷卻用 空氣的流動，使得在多個翼片部的各個之中使冷卻用空氣 在各翼片間減速而大致均勻地流動；以及排出冷卻用空氣 的排出口 7。 φ 即，多個翼片部3沿底板2的寬度方向被配置，隔板 部4被配置在翼片部3之間及兩外側端部，擋板部5— 1、 5- 2與.各翼片部的最近端部及最遠端部的板狀翼片連接被 配置。 熱交換器10，在通過隔板部隔開的空間內，在底板的 寬度方向上並列配置有散熱部件，上述散熱部件沿長度方 向配置有多個板狀翼片。在每個散熱部件上，從各自的入 口部送入高速的空氣流8。由於在最近前的板狀翼片3上 • 安裝有擋板部5 - 1，因此由擋板部阻礙流動，高速的空氣 流8，沿著通過沿底板部的長度方向並列配置的多個板狀 翼片的一側的端部和隔板部4形成的通路流動。 上述的高速的空氣流8，撃打被安裝在最遠處的板狀 翼片上的擋板部5 - 2而打亂流動，由擋板部5 - 2及隔板 部4引導，改變方向，降低速度行程低速的空氣流9，在 板狀翼片3間流動，在由沿底板部2的長度方向並列配置 的多個板狀翼片的另一側的端部和隔板部4形成的通路處 進行合流，從排出口 7被排出到熱交換器外。如此在沿長 -15- 200819701 (13) 度方向被配置的多個板狀翼片的全部之間，冷的冷卻用空 氣流動。 在該方式的熱交換器中，如參照圖4說明的那樣，也 要求板狀翼片的間隔、板狀翼片的長度、在板狀翼片間流 * 動的冷卻空氣的流速的關係，散熱效率良好。即，如上上 " 述，若設板狀翼片的間隔爲d(mm)，板狀翼片的長度爲 L(m)，在板狀翼片間流動的冷卻空氣的流速爲v(m/s)，則 φ 9.4亦/v)x3。更優選的是d $ 9.4亦/—v)x2。最優選的是d € 9.4"(L/v)。 通過利用圖3所示方式的熱交換器，不僅是沿底板的 長度方向的多個發熱零件的散熱，還可以有效進行在寬度 方向上配置的多個發熱零件的散熱，適合各種發熱零件的 冷卻、散熱，其適用範圍擴大。 圖7(a)是說明本發明的熱交換器的其他方式的局部 立體圖。圖7(b)是俯視圖。在該方式中，擋板部5A被 φ 配置成朝向裏側與板狀翼片3之間的間隔逐漸變小，而 且，在翼片上部還配置有擋板部5 D。因此，冷卻用空氣 被擋板引導而改變方向並減速，在板狀翼片3間流動。在 圖7(a)所示的方式中，板狀翼片3相對於風向（從近前 朝向裏側）呈直角配置。板狀翼片3如圖7 ( b )所示也可 以相對於風向傾斜配置。 即，如圖7所示，通過在翼片上部還設置擋板，可以 將翼片的高度設定成低於圖1所示的方式中的空氣取入 口，翼片效率變高，在熱特性上更加優選。 -16- 200819701 (14) 另外，以促進熱傳遞爲目的，在翼片附近設置棒狀的 部件，或在翼片上開設1個或多個槽，將流路做成曲柄狀 (2個L字狀）也能呈現效果。 圖8是說明本發明的熱交換器的其他的一個方式的局 * 部立體圖。如圖8所示，在底板部2上，在縱向上以規定 ' 間隔配置有多個板狀翼片3，從而形成翼片部17。上述2 個翼片部1 7相對於入口部配置成八字形，從而形成由i φ 對翼片部構成的翼片群1 8。八字形被配置成，沿冷卻用空 氣（高速）8從入口部向排出口逐漸變窄。若八字的頂部 分的板狀翼片相互接觸進行配置，則鄰接的板狀翼片的橫 方向的間隔被關閉，冷卻用空氣的流動在橫方向上被引 導。如圖8所示，通過使位於由1對翼片部構成的翼片群 1 8的左側的最前方的板狀翼片3和位於鄰接的翼片群1 8 的右側的最前方的板狀翼片3相接觸配置，由此可以將冷 卻用空氣的流動引導向八字形的內側。 φ 如上上述，若在底板部上並列配置由1對翼片部構成 的翼片群18，則不必使用擋板部及隔板部，也能使高速的 冷卻用空氣8在各翼片間減速且大致均勻地流動。 圖9是說明本發明的熱交換器的其他的一個方式的俯 視圖。如圖9所示，在該方式中，參照圖8說明了的方式 •(即，2個翼片部1 7相對於入口部呈八字形配置而形成 的由1對翼片部構成的翼片群18)的八字的頂部分的鄰接 的板狀翼片3的橫方向的間隔打開，在其排出口側設置有 沿高速的冷卻用空氣的氣流8被配置的1對翼片（即，直 -17· 200819701 (15) 行翼片）1 9。即使在設置有直行翼片的情況下，在熱設計 上關於參數z，由於同等地設計z=y，2々(ak/v)，因此性能也 不會下降。即，在該方式中，也不必使用擋板部及隔板 部，如符號9所示，也能使高速的冷卻用空氣8在各翼片 ^ 間減速且大致均勻地流動。另外，若像這樣設置直行翼 ' 片，則即使在風速發生變化的情況下也能使熱性能穩定。 圖10是說明用於本發明的熱交換器的翼片部的製造 φ 方法的一個方式的圖。如圖10(a)所示，通過擠壓成形 等的方法，形成一種板狀翼片3，上述板狀翼片3在各個 面上分別具有形成嵌合構造的突起部2 1及凹部2 0。其 次，將多個板狀翼片，使突起部21嵌合於鄰接翼片的凹 部20。所謂底板部2如符號D所示，與板狀翼片的基部 熱連接以使熱傳導良好。如符號E所示，嵌合構造成爲防 止焊料上升的構造。另外，除了擠壓成形外，可以對於鋁 材通過衝壓加工（熱間或冷間）形成翼片，可以層疊將板 馨 沖孔加工成沖孔金屬（punching metal )狀後的板來形成 翼片部分。而且也可以通過機械加工形成翼片，通過對厚 板狀的鋁材進行衝壓加工（熱間或冷間），也能採用使棒 狀的翼片立在基底上的加工。首先如圖1 0 ( a )所示，在 鄰接翼片的凹部20上嵌合突起部21，其次，如圖10 (b )所示，將被嵌合的翼片在以符號F表示的寬度上切 斷作爲翼片部使用。另外F例如爲3〜20mm左右的尺 寸。 典型的尺寸爲：翼片間隔〇.5mm，翼片厚度1 -18- 200819701 (16) 3mm，翼片長度3〜7mm，翼片局度3〜60mm，[翼片厚 度]/[翼片間隔]=1〜3。另外，相對於在散熱器（heat sink )入口的冷卻風的方向，有時將翼片的方向設置成 30°左右，也有時通過將在散熱器入口的翼片的外觀上的 厚度相對於入口整體限制在3 0 %左右，從而實現壓力損失 降低。但這只不過是一個例子，並不是限定本發明發揮效 果的範圍。 圖1 1是說明將熱交換器應用於直接火烤用的鍋的情 況的圖。圖11(a)表示翼片22。在底板部2上以規定的 間隔配置有翼片3。圖1 1 ( b )表示將翼片設置在直接火 烤用的鍋的下側進行熱交換的狀態。如圖11 ( b )所示， 例如，將配置成八字形的翼片對，以八字的頂部朝向鍋的 外周的方式配置成星型。通過像這樣配置在直接火烤用的 鍋的下側，能使熱交換的效率提高3 0〜5 0 %，能使燃料 (或柴火）的使用量降低1 /2〜2/3，作爲地球溫暖化對策 的一環對削減C02也能做出貢獻。另外上述熱交換器也可 以是獨立於鍋的其他部件，可以只在使用時接觸利用。 本發明的熱交換器，還可以應用于自然空冷、水冷的 任一種的交換器中。即，在自然空冷下，能使被交換的熱 量提高10%。另外在水冷的熱交換器中，能使熱傳遞率提 高 2 5 %。 典型的尺寸爲：翼片間隔2mm，翼片厚度1〜3mm， 翼片長度3〜7mm，翼片高度3〜60mm，[翼片厚度]/[翼片 間隔]=1〜2。這只是表示一例，並非是限定本發明發揮效 -19- 200819701 (17) 果的範圍。 根據本發明，基於確定的包絡體積、確定的風量，使 發熱零件的溫度下降，並且也能使流體的壓力損失降低。 即、在同一包絡體積下冷卻能力高，在上風下風方向上不 會產生大致溫度差即能獲得即使在下風冷空氣也會進入的 • 散熱效率良好的熱交換器。尤其，在配置翼片的底板長的 熱父換器的情況下，能獲得散熱效率顯著優良的熱交換 _ .器。 【圖式簡單說明】 圖1是說明本發明的熱交換器的局部立體圖； 圖2是說明圖1所示的方式的熱交換器的俯視圖； 圖3是說明具有多個翼片部的本發明的其他的一個方 式的熱交換器的立體圖； 圖4是說明本發明的熱交換器的散熱特性的局部剖面 圖； 圖5是說明現有的熱交換器的散熱特性的局部剖面 圖， 圖6是表示現有的熱交換器的立體圖； 圖7是說明本發明的其他方式的局部立體圖； 圖8是說明本發明的熱交換器的其他的一個方式的局 部立體圖； 圖9是說明本發明的熱交換器的其他的一個方式的俯 視圖， -20- 200819701 (18) 圖1 〇是說明用於本發明的熱交換器的翼片部的製造 方法的一個方式的圖； 圖11是說明將熱交換器應用於直接火烤用的鍋的情 況的圖。BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a heat exchanger having excellent heat dissipation efficiency, and particularly to improving the flow of cooling air flowing between the fins and the heat between the fins. An exchange of heat exchangers consisting of base plate fins. [Prior Art] Increased heat generation and heat generation density of CPU, components, etc. A high-performance heat exchanger with good heat dissipation efficiency. At present, a heat exchanger consisting of an extruded profile of aluminum which is inexpensive to manufacture. The heat exchanger of the profile is easy to manufacture due to the formation of the bottom plate and the heat dissipating fins. In addition, the bottom plate and the heat dissipating fins are manufactured separately, and the heat dissipating fins are joined on one side to manufacture a heat exchanger. Fig. 6 is a perspective view showing a conventional heat exchanger. As shown in Fig. 6, the conventional heat exchanger 100 has a heat radiating bottom plate 120 on one side and a plurality of heat fins 1 3 thermally connected to the other side of the bottom plate. In the conventional heat exchanger, the cooling air is blown from the end of one side to the bottom of the bottom plate by a fan or the like as indicated by reference numeral 108, and the heat conducted from the member to the heat radiating fins through the bottom plate is radiated to the atmosphere. When a plurality of heat-generating components are thermally connected to the longitudinal direction of the bottom plate, the heat of the plurality of heat-generating components is radiated, and a large amount of cooling air is blown from the end portion to the plate-shaped heat-dissipating fins (refer to 曰本特开平7_ Deceleration and heat dissipation are required to be directly utilized by the extruded body, as shown by the bottom plate, the plate-like dispersion length of the part is heated to zero. The edge is in order to make the side of the -15160 200819701 (2) bulletin. In the above-described heat exchanger in which a plurality of plate-shaped heat radiating fins are thermally connected to one surface of the bottom plate, generally, the amount of cooling air to be supplied is determined by each device. If the length of the plate-shaped fins is long and the interval between the fins is small, cold air will hit the front fins but the cold air will not hit the inner fins. On the other hand, if the interval between the plate-like fins is made large, the cooling efficiency is expected, and a large amount of cooling air flow is blown toward the fins at a high speed φ, and heat is exchanged because air passes only through the central portion between the fins. Insufficient skin condition. Therefore, in the conventional method of cooling a heat exchanger, there is a problem in that heat of a plurality of heat-generating components disposed over the depth, particularly heat of a downdraft heat-generating component, cannot be effectively cooled. SUMMARY OF THE INVENTION Accordingly, it is an object of the present invention to provide a heat exchanger which is capable of efficiently cooling a plurality of heat-generating components arranged over a depth and having good heat dissipation efficiency. # Inventors conducted repeated investigations to solve the above-mentioned problems. The result is determined that if the flow rate of the cooling air flowing between the plate fins is lowered, the temperature boundary layer is made (i.e., when the air flows through the fins, the heat of the fins is transmitted, and the temperature of a part of the air flow rises. , creating a boundary between the portion of the air flow that is not affected by the heat of the fins. The boundary layer at this time is referred to as a temperature boundary layer), so that the temperature of the surface of the plate-like fin of the heat exchanger is close to At the temperature on the exit side of the fin. That is, it is determined that even if a high-speed cooling air flow is blown as much as possible between the plate-like fins, a considerable portion of the cooling air flow is independent of heat exchange only -5-200819701 (3) is simply passed through the plate-like fins In order to improve the heat dissipation efficiency, it is necessary to appropriately set the relationship between the interval of the plate-like fins, the length of the plate-like fins, and the flow velocity of the cooling air flowing between the plate-like fins. The present invention has been made based on the above findings. A first aspect of the heat exchanger according to the present invention is a heat exchanger having a bottom plate portion that is thermally connected to at least one heat generating component on one surface, and at least one fin portion. The longitudinal direction of the other surface of the bottom plate portion is arranged at a predetermined angle and is formed by a plurality of fins that are thermally connected to the bottom plate; and the inlet portion is cooled to the at least one of the fin portions. The air; the baffle portion and the partition portion guide the flow of the cooling air so that the cooling air is decelerated between the fins and flows substantially uniformly among the at least one of the fin portions; And a discharge port that discharges cooling air. According to a second aspect of the heat exchanger of the present invention, there is provided a heat exchanger including: at least one fin portion including a plurality of fins; and an inlet portion that is respectively provided to the at least one fin portion Cooling air is supplied; the baffle portion and the partition portion guide the flow of the cooling air so that the cooling air is decelerated between the fins and substantially uniform among the at least one of the fin portions The ground flows; and the discharge port, which discharges the cooling air. A third aspect of the heat exchanger according to the present invention is the heat exchanger comprising: a bottom plate portion thermally connected to at least one heat generating component; and a fin group in which at least two fin portions are disposed to form The structure for decelerating the flow rate of the cooling air flowing between the fins, wherein the at least two fin portions are arranged side by side at a predetermined angle along the longitudinal direction of the bottom plate portion and are composed of -6-200819701 (4) and a plurality of fins thermally connected to the bottom plate; an inlet portion that supplies cooling air to each of the at least two fin portions; and a discharge port that discharges cooling air to arrange the fin group to guide the cooling The flow of air causes the cooling air to decelerate between the fins in each of the at least two fin portions to flow substantially uniformly. The fourth aspect of the heat exchanger according to the present invention is a heat exchanger configured to decelerate the flow rate of the cooling air so as to gradually narrow from the inlet φ port to the discharge port. Eight-character. According to a fifth aspect of the heat exchanger of the present invention, in the heat exchanger, the fin group is arranged in a figure-eight shape so as to gradually narrow from the inlet portion to the discharge port, and the discharge port of the fin group is The side also has at least one pair of fins disposed in the longitudinal direction of the bottom plate. According to a sixth aspect of the heat exchanger of the present invention, at least one of the fin portions is constituted by one fin portion, and the partition portion is disposed at both end portions of the fin portion. The baffle portion is disposed in the vicinity of the flaps at the most proximal end portion and the most distal end portion. According to a seventh aspect of the present invention, in the heat exchanger, the at least one fin portion is configured by a plurality of fin portions arranged along a width direction of the bottom plate, and the partition portion is disposed on the wing The baffle portions are disposed between the sheet portions and the outer end portions of the respective fin portions in the vicinity of the fins at the most proximal end portion and the farthmost end portion of each of the fin portions. According to a eighth aspect of the heat exchanger of the present invention, the cooling air that is fed into the radiator from the inlet at a high speed flows along a passage, and the passage is formed in the plurality of fins along the partition portion. Between the end of the one end 200819701 (5) and the partition portion, the cooling air is guided by the baffle portion and the partition portion to be decelerated, and flows between the fins, along the plurality of fins. A passage formed between the other end portion and the partition portion flows, and is discharged from the discharge port. The ninth aspect of the heat exchanger according to the present invention is a heat exchanger that sets the fin spacing, the fin length, and the flow velocity between the fins so that the fins transmitting the heat of the heat generating component are The difference between the temperature of the sheet surface and the temperature of the cooling air at the upper φ discharge port becomes small. A first aspect of the heat exchanger according to the present invention is a heat exchanger that decelerates the cooling air flowing between the fins so as to be adjacent to each other by the cooling air flowing between the fins The respective temperature boundary layers of the fins overlap. The first aspect of the heat exchanger according to the present invention is a heat exchanger in which the fin spacing is d (mm), the fin length is L (m), and the flow velocity between the fins is v (m/). s), dS 9.4V57^)x3. The first aspect of the heat exchanger according to the present invention is such that the heat exchanger 'haves a fin spacing of d (mm), a fin length of L (m), and a flow velocity between the fins of v (m). /s), dg 9.4V5^x2. According to a third aspect of the heat exchanger of the present invention, the heat exchanger of the following is characterized in that the fin spacing is d (mm), the fin length is L (m), and the flow velocity between the fins is v (m/). s ), dg 9.4^(l/v). According to a fourteenth aspect of the present invention, in the heat exchanger, the flow rate of the cooling air flowing through the plurality of fin portions and/or the flow rate of the cooling air flowing between the fins is different. -8-200819701 (6) A fifteenth aspect of the heat exchanger according to the present invention is the following heat exchanger. The heat exchanger is a naturally air-cooled heat exchanger. A sixteenth aspect of the heat exchanger according to the present invention is the following heat exchanger. The heat exchanger is a water-cooled heat exchanger. [Embodiment] A heat exchanger of the present invention will be described with reference to the drawings. φ One embodiment of the heat exchanger according to the present invention is a heat exchanger having a bottom plate portion thermally connected to at least one heat generating component on one surface; at least one fin portion, which is edged The longitudinal direction of the other surface of the bottom plate portion is arranged at a predetermined angle and is formed by a plurality of fins that are thermally connected to the bottom plate; and the inlet portion is sent to the at least one of the fin portions for cooling. The air; the baffle portion and the partition portion guide the flow of the cooling air so that the cooling air is decelerated between the fins in each of the at least one fin portion, and flows substantially uniformly; And the discharge # port, which discharges the cooling air. For example, in one embodiment, at least one of the fin portions is constituted by one fin portion, the partition portion is disposed at both end portions of the flap portion, and the baffle portion is disposed at the most proximal end and the farthest end. Near the plate-like fins of the part. In the following description, the plate-like fins, the fin portions, and the fin groups used in the present invention are defined as follows. That is, each of the plate-like fins is a flap indicated by reference numeral 3 in Fig. 1, and the flap portion is as shown in Fig. 1, which means that the plurality of plate-like fins 3 are arranged in the longitudinal direction and are arranged in a row. overall. The wing group refers to a knot -9 - 200819701 (7) formed by two fin portions arranged in a substantially figure-eight shape, as shown in Fig. 8 'the wing portion is represented by the symbol 17 'the wing group by the symbol 1 8 indicates. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a partial perspective view showing a heat exchanger of the present invention. As shown in Fig. 1, the heat exchanger of the present invention has a bottom plate portion 2' which is connected to a heat-generating component (not shown) on the back surface, and a fin portion which is formed by a length along the surface of the bottom plate portion. The plurality of plate-like fins 3 arranged in parallel at a predetermined angle; the inlet portion 6 for supplying cooling air to the fin portion 3; the baffle portions 5 φ-1, 5-2 and (not shown) The partition portion guides the flow of the cooling air so that the cooling air is decelerated between the fins of the fin portion, and flows substantially uniformly, and the discharge port 7 for discharging the cooling air is discharged. In Fig. 1, a high velocity air stream is fed from the inlet portion 6 (i.e., the inlet on the surface), and a low velocity air stream is fed between the fins (i.e., the actual inlet). Fig. 2 is a plan view showing a heat exchanger of the embodiment shown in Fig. 1; As shown in Fig. 2, a plurality of plate-like fins 3 are arranged side by side in the longitudinal direction at a predetermined angle on the bottom plate portion 2. Arrange the adjacent plate-like wing φ pieces at regular intervals. Although omitted in Fig. 1 for ease of explanation, the partition portion 4 is provided at both end portions of the bottom plate portion 2. On the most recent plate-like fins and the innermost plate-like fins, baffle portions 5 - i, 5 - 2 are respectively provided. The heat exchanger is provided with an inlet portion for introducing an air flow and a discharge port for discharging the air flow. A high velocity air stream 8 is fed from the inlet to the heat exchanger. Since the baffle portion 5 - 1 is attached to the recent plate-like fin 3 , the air flow is blocked by the baffle portion, and the high-speed air flow 8 is formed along a plurality of plates arranged in parallel along the longitudinal direction of the bottom plate portion. The end of one side of the flap and the passage formed by the partition portion 4 flow. -10- 200819701 (8) The above-mentioned high-speed air flow 8 is used to smash the baffle portion 5.2 attached to the farthest plate-like fin to disturb the flow, and the baffle portion 5-2 and the partition portion 4 guiding, changing direction, decreasing speed to form a low-speed air flow 9, flowing between the plate-like fins 3, at the other end of the plurality of plate-like fins arranged side by side along the longitudinal direction of the bottom plate portion 2 The passage formed by the partition portion 4 merges and is discharged from the discharge port 7 to the outside of the heat exchanger (indicated by reference numeral 11). φ Referring to Fig. 4 and Fig. 5, the heat dissipation characteristics of the heat exchanger of the present invention and the conventional heat exchanger will be described in comparison. Fig. 4 is a partial cross-sectional view showing the heat dissipation characteristics of the heat exchanger of the present invention. Fig. 5 is a partial cross-sectional view showing heat dissipation characteristics of a conventional heat exchanger. In the left side portions of Figs. 4 and 5, the boundary layer of the temperature boundary layer formed by the flow of cooling air between the plate fins is shown (i.e., the heat transfer of the fins when air flows between the fins, air) The temperature of a part of the flow rises, and a boundary φ is created between the portion of the air flow that is not affected by the heat of the fin. The boundary layer at this time is referred to as a temperature boundary layer. The relationship between the fin spacing and the temperature distribution is shown on the right side of Figs. 4 and 5 . In the conventional heat exchanger shown in Fig. 5, the interval between the plate-like fins 3 is large, and a high-speed cooling air flow is blown between the plate-like fins. That is, between the temperature boundary layers 15, 5, there is a space of the flowing air flow irrespective of heat exchange, the temperature on the surface of the fin is high, and the portion of the flowing air flow irrespective of heat exchange is kept in cooling The temperature of the air flow does not rise. In this way, even if a high-speed cooling air flow is blown between the plate-like fins, a considerable portion of the cooling air flow is generated regardless of the heat exchange, but simply passes through the -11 - 200819701 (9) between the plate-like fins State (see symbol 16). As shown in the right side portion of Fig. 5, the temperature is high on the surface of the plate-like fin, and the temperature does not rise at all in the central portion between the plate-like fins. That is, the temperature difference becomes very large. Therefore, even if a high-speed cooling air flow is blown, the temperature of the surface of the fin does not decrease, and it is apparent that the heat dissipation efficiency is extremely poor. In the heat exchanger of the present invention shown in Fig. 4, the flow of the cooling air is not blown into the fins at a high speed, and if the flow rate of the φ cooling air flowing between the plate-like fins 3 is lowered, the temperature boundary layer 15 is caused. The coincidence enables the temperature of the surface of the plate-like fin of the heat exchanger to be close to the temperature at the outlet side of the fin. That is, as shown in the right side portion of Fig. 4, the temperature of the surface of the plate-like fin is lowered, and the temperature rise can be seen even in the central portion between the plate-like fins. That is, the difference between the temperature of the surface of the plate-like fin and the temperature of the central portion between the fins is small, and therefore, the temperature of the surface of the fin is lowered, and the heat dissipating efficiency is remarkable. Φ The heat exchanger having a good heat dissipation efficiency described with reference to Fig. 4 must appropriately require the interval between the plate-like fins, the length of the plate-like fins, and the relationship between the flow rates of the cooling air flowing between the plate-like fins. As shown in FIG. 4, from the condition of making the temperature boundary layers coincide (that is, making the temperature boundary layer thick enough), if the interval of the plate-like fins is d (mm), the plate-like fins The length is L (m), and the flow rate of the cooling air flowing between the plate fins is v (m / s), then becomes d - 2 - 22 * 10_6] (L / v) = 9.4 * 10 -3 J(L/v) -12- 200819701 (10) The fin spacing d becomes d=9A^J^/v). In the present invention, d S 3 . More preferred is d S 9.4V57^)x 2 . Further preferred is 9.4 V (L/v). The essence of the present invention is that the shape of the fins and the wind speed are appropriately required. For convenience of explanation, the description has been made on the case where the surface of the fin is a flat flat fin, but the effect of the present invention is not limited to the flat fin. The lattice type fins, the knurled fins (wings having irregularities on the surface), the pin fins, and the fins having undulations in the upwind and downwind directions also have the same effects. The U-shaped curve shown in Figs. 4 and 5 will be described in detail below. If the length from the entrance of the airfoil is X, the distance from the surface of the airfoil is y, the air temperature is T(x, t), the airfoil temperature is T0, the flow velocity of the main flow is V, and the thermal diffusivity is a', then The relationship between the air temperature and the fin temperature can be expressed by T(x, t) = T0*erfc(z), z =: y/2/^/(ax/v). Where z represents the substantial distance from the airfoil. Also, considering the influence from adjacent fins, if the fin spacing is d, then T(x, t) = TO* ( erfc(z) + erfc(z')), z = (dy) / 2/^(ax/v), the 11-character curve shown in Fig. 4 and Fig. 5 is obtained. As described above, the substantial distance z from the fin can be regarded as z = y / 2 / V (ax / v), so the 値 can be designed as a parameter. -13- 200819701 (11) The average temperature of the fin relative to the exhaust gas temperature is 2.65 times for z = 3, 1.79 times for z = 2, and 1.12 times for z = l. Preferably z < 3, more preferably z < 2, most preferably z < As a typical crucible, the fin spacing is 0 · 5 m m to 1 m m, the fin thickness is 1 mm to 2 mm, and the fin thickness is selected to be about twice the fin spacing. In addition, as the length of the fin is about 3 to 20 mm. Further, 迨 is merely an example and is not intended to limit the scope of the effect of the present invention. φ Another aspect of the heat exchanger according to the present invention is a heat exchanger having a bottom plate portion thermally connected to a heat generating component on one surface, and a plurality of fin portions being provided along the bottom plate portion The other side surface of the other side is formed by a plurality of plate-like fins arranged side by side at a predetermined angle; the inlet portion is supplied with cooling air to the plurality of fin portions, and the baffle portion and the partition portion are guided to cool. The flow of air causes the cooling air to be decelerated between the fins to flow substantially uniformly among the plurality of fin portions, and the discharge port for the cooling air is discharged. # A plurality of fin portions are arranged along the width direction of the bottom plate, and the partition portion is disposed between the fin portions and the both outer end portions, and the plate end portion of the baffle portion and the proximal end portion and the most distal end portion of each fin portion The fins are connected and configured. Fig. 3 is a perspective view showing another heat exchanger of the present invention having a plurality of fin portions. As shown in Fig. 3, in the heat exchanger 10 of this embodiment, a plurality of heat exchangers 1 described with reference to Fig. 1 are arranged in parallel in the width direction of the bottom plate, and the heat exchanger 1 is partitioned by a partition portion and a baffle portion. Surrounding, and a plurality of plate-like fins are arranged along the longitudinal direction of the bottom plate. That is, a heat exchanger has a bottom plate portion 2 which is thermally connected to a heat-generating component (not shown) on one side surface 14-200819701 (12); a plurality of fin portions which are formed along the bottom plate portion The other side surface is formed by a plurality of plate-like fins 3 arranged side by side at a predetermined angle in the longitudinal direction; the inlet portion 6 is supplied with cooling air to the plurality of fin portions; the baffle portion 51-1, 5-2 And the partition portion 4 guides the flow of the cooling air so that the cooling air is decelerated between the fins to substantially uniformly flow among the plurality of fin portions, and the discharge port 7 for discharging the cooling air is discharged. . φ That is, the plurality of fin portions 3 are arranged along the width direction of the bottom plate 2, and the partition portion 4 is disposed between the flap portions 3 and both outer end portions, and the baffle portions 5-1, 5- 2 and each The plate-like fin connection of the proximal end and the most distal end of the flap portion is configured. In the heat exchanger 10, a heat dissipating member is arranged in parallel in the width direction of the bottom plate in a space partitioned by the partition portion, and the heat radiating member has a plurality of plate-like fins arranged in the longitudinal direction. On each of the heat dissipating members, a high velocity air stream 8 is fed from the respective inlet portions. Since the shutter portion 5-1 is attached to the recent plate-like fin 3, the flow is blocked by the shutter portion, and the high-speed air flow 8 is along the plurality of plates arranged in parallel along the longitudinal direction of the bottom plate portion. The end of one side of the flap and the passage formed by the partition portion 4 flow. The high-speed air flow 8 described above is smashed by the baffle portion 5.2 attached to the plate fin of the farthest portion, and is disturbed by the baffle portion 5-2 and the partition portion 4, and the direction is changed and lowered. The air flow 9 having a low speed stroke flows between the plate-like fins 3, and the passage formed by the other end portion of the plurality of plate-like fins arranged side by side in the longitudinal direction of the bottom plate portion 2 and the partition portion 4 At the same time, the flow is merged and discharged from the discharge port 7 to the outside of the heat exchanger. Thus, between the plurality of plate-like fins arranged along the length of -15 - 200819701 (13), cold cooling flows with air. In the heat exchanger of this aspect, as described with reference to Fig. 4, the relationship between the interval of the plate-like fins, the length of the plate-like fins, and the flow velocity of the cooling air flowing between the plate-like fins is also required. The heat dissipation efficiency is good. That is, as described above, if the interval between the plate-like fins is d (mm), the length of the plate-like fins is L (m), and the flow rate of the cooling air flowing between the plate-like fins is v (m) /s), then φ 9.4 is also /v)x3. More preferably, d $ 9.4 is also / -v) x2. Most preferred is d € 9.4 " (L/v). By using the heat exchanger of the embodiment shown in FIG. 3, not only heat dissipation of a plurality of heat-generating components along the longitudinal direction of the bottom plate but also heat dissipation of a plurality of heat-generating components arranged in the width direction can be effectively performed, and cooling of various heat-generating components can be performed. , heat dissipation, its scope of application is expanded. Fig. 7 (a) is a partial perspective view showing another embodiment of the heat exchanger of the present invention. Fig. 7(b) is a plan view. In this embodiment, the shutter portion 5A is disposed such that the interval between the rear side and the plate-like fin 3 gradually decreases, and the shutter portion 5D is disposed on the upper portion of the flap. Therefore, the cooling air is guided by the baffle to change direction and decelerate, and flows between the plate-like fins 3. In the mode shown in Fig. 7 (a), the plate-like fins 3 are arranged at right angles with respect to the wind direction (from the front side toward the back side). The plate-like fins 3 can also be arranged obliquely with respect to the wind direction as shown in Fig. 7(b). That is, as shown in Fig. 7, by providing a baffle on the upper portion of the fin, the height of the fin can be set lower than that of the air intake port in the manner shown in Fig. 1, and the fin efficiency becomes high, in terms of thermal characteristics. More preferred. -16- 200819701 (14) In addition, for the purpose of promoting heat transfer, a rod-shaped member is provided in the vicinity of the fin, or one or a plurality of grooves are formed in the fin, and the flow path is formed into a crank shape (two L characters). Shape) can also show effects. Fig. 8 is a perspective view showing another embodiment of the heat exchanger according to the present invention. As shown in Fig. 8, on the bottom plate portion 2, a plurality of plate-like fins 3 are arranged at predetermined intervals in the longitudinal direction to form the flap portions 17. The two fin portions 17 are arranged in a figure-eight shape with respect to the entrance portion, thereby forming a fin group 18 composed of i φ for the fin portions. The figure-eight shape is arranged to be gradually narrowed from the inlet portion to the discharge port along the cooling air (high speed) 8. When the plate-like fins at the top of the figure are placed in contact with each other, the interval in the lateral direction of the adjacent plate-like fins is closed, and the flow of the cooling air is guided in the lateral direction. As shown in Fig. 8, the frontmost plate-like fin 3 located on the left side of the airfoil group 18 composed of the pair of fin portions and the frontmost plate shape on the right side of the adjacent fin group 18 are provided. The fins 3 are in contact with each other, whereby the flow of the cooling air can be directed to the inside of the figure-eight. φ As described above, when the fin group 18 composed of one pair of fin portions is arranged in parallel on the bottom plate portion, the high-speed cooling air 8 can be decelerated between the fins without using the baffle portion and the partition portion. And flow roughly evenly. Fig. 9 is a plan view showing another embodiment of the heat exchanger of the present invention. As shown in Fig. 9, in this embodiment, the method described with reference to Fig. 8 (i.e., the fins formed by the pair of fin portions formed by arranging the two fin portions 17 in a figure-eight shape with respect to the entrance portion) The horizontally adjacent plate-like fins 3 of the top portion of the splayed group of the group 18) are opened in the lateral direction, and a pair of fins (i.e., straight) in which the airflow 8 of the high-speed cooling air is disposed is provided on the discharge port side. -17· 200819701 (15) Line fins) 19. Even in the case where a straight fin is provided, in terms of thermal design with respect to the parameter z, since z = y, 2 々 (ak / v) is equally designed, the performance is not degraded. In other words, in this embodiment, it is not necessary to use the baffle portion and the partition portion, and as shown by the reference numeral 9, the high-speed cooling air 8 can be decelerated between the fins and flow substantially uniformly. Further, if the straight-wing blade is provided as described above, the thermal performance can be stabilized even when the wind speed changes. Fig. 10 is a view for explaining one mode of a method of manufacturing φ of a fin portion used in the heat exchanger of the present invention. As shown in Fig. 10 (a), a plate-like fin 3 is formed by a method such as extrusion molding, and the plate-like fins 3 have projections 2 1 and recesses 20 each having a fitting structure on each surface. . Next, the plurality of plate-like fins are fitted to the concave portion 20 of the adjacent fins. The bottom plate portion 2 is thermally connected to the base of the plate-like fin as indicated by the symbol D to provide good heat conduction. As shown by the symbol E, the fitting structure is a structure for preventing the solder from rising. Further, in addition to extrusion molding, the fins may be formed by press working (hot or cold) on the aluminum material, and the sheets which are punched and punched into a punching metal may be laminated to form the fins. section. Further, the fins may be formed by machining, and the processing of the rod-shaped fins on the base may be employed by press working (hot or cold) on the thick aluminum plate. First, as shown in Fig. 10(a), the projections 21 are fitted to the recesses 20 of the adjacent fins, and secondly, as shown in Fig. 10(b), the fins to be fitted are at the width indicated by the symbol F. The upper cut is used as a flap portion. Further, F is, for example, a size of about 3 to 20 mm. Typical dimensions are: fin spacing 〇5mm, fin thickness 1 -18- 200819701 (16) 3mm, wing length 3~7mm, wing stiffness 3~60mm, [wing thickness] / [wing spacing ]=1~3. Further, the direction of the fins may be set to about 30° with respect to the direction of the cooling air at the inlet of the heat sink, and sometimes the thickness of the fins at the inlet of the radiator may be relative to the entrance. The overall limit is around 30%, resulting in a reduction in pressure loss. However, this is only an example and is not intended to limit the scope of the invention. Fig. 11 is a view for explaining a case where a heat exchanger is applied to a pan for direct fire baking. Figure 11 (a) shows the flap 22. The fins 3 are arranged at predetermined intervals on the bottom plate portion 2. Fig. 1 1 (b) shows a state in which the fins are placed on the lower side of the pan for direct fire for heat exchange. As shown in Fig. 11 (b), for example, the pair of fins arranged in a figure-eight shape is arranged in a star shape so that the top of the figure is oriented toward the outer circumference of the pot. By arranging the lower side of the pan for direct fire baking, the efficiency of heat exchange can be increased by 30 to 50%, and the amount of fuel (or firewood) can be reduced by 1 /2 to 2/3 as the earth. A part of the warming measures can also contribute to the reduction of CO2. Further, the above heat exchanger may be other components independent of the pot, and may be used only in contact at the time of use. The heat exchanger of the present invention can also be applied to an exchanger which is naturally air-cooled or water-cooled. That is, under natural air cooling, the amount of heat exchanged can be increased by 10%. In addition, in a water-cooled heat exchanger, the heat transfer rate can be increased by 25 %. Typical dimensions are: fin spacing 2 mm, fin thickness 1 to 3 mm, fin length 3 to 7 mm, fin height 3 to 60 mm, [wing thickness] / [flap spacing] = 1 to 2. This is merely an example and is not intended to limit the scope of the invention to effect -19-200819701 (17). According to the present invention, the temperature of the heat generating component is lowered based on the determined envelope volume and the determined air volume, and the pressure loss of the fluid can also be lowered. That is, the cooling capacity is high in the same envelope volume, and the heat temperature is good even if there is no approximate temperature difference in the upwind downwind direction. In particular, in the case of a hot parent device in which the bottom plate of the fin is disposed, a heat exchange device having remarkably excellent heat dissipation efficiency can be obtained. BRIEF DESCRIPTION OF THE DRAWINGS Fig. 1 is a partial perspective view showing a heat exchanger according to the present invention; Fig. 2 is a plan view showing a heat exchanger of the mode shown in Fig. 1. Fig. 3 is a view showing the present invention having a plurality of fin portions. Fig. 4 is a partial cross-sectional view showing heat dissipation characteristics of the heat exchanger of the present invention; Fig. 5 is a partial cross-sectional view showing heat dissipation characteristics of the conventional heat exchanger, Fig. 6 is Fig. 7 is a partial perspective view showing another embodiment of the present invention; Fig. 8 is a partial perspective view showing another mode of the heat exchanger according to the present invention; and Fig. 9 is a view showing heat exchange of the present invention. Top view of another mode of the device, -20-200819701 (18) FIG. 1 is a view illustrating one mode of a method for manufacturing a fin portion of a heat exchanger according to the present invention; FIG. 11 is a view illustrating a heat exchanger A diagram of the case of a pot for direct fire baking.
【主要元件符號說明】 d :間隔 T :空氣溫度 T0 :翼片溫度 1 :熱交換器 2 :底板部 3 :翼片部 4 :隔板部 5A :擋板部 5D :擋板部 5 - 1 :擋板部 5 - 2 :擋板部 6 :入口部 7 :排出口 8 :空氣流 9 :空氣流 1 〇 :熱交換器 1 5 :溫度邊界層 1 7 :翼片部 -21 - 200819701 (19) 18 :翼片群 1 9 :翼片 20 :凹部 21 :突起部 ' 22 :翼片[Description of main component symbols] d: Interval T: Air temperature T0: Foil temperature 1: Heat exchanger 2: Base plate 3: Flap portion 4: Partition portion 5A: Baffle portion 5D: Baffle portion 5 - 1 : baffle portion 5 - 2 : baffle portion 6 : inlet portion 7 : discharge port 8 : air flow 9 : air flow 1 〇 : heat exchanger 1 5 : temperature boundary layer 1 7 : fin portion - 21 - 200819701 ( 19) 18: Flap group 19: Flap 20: Recess 21: Protrusion '22: Flap
-22--twenty two-