Γ 200301343 玫、發明說明 (發明說明應敘明：發明所屬之技術領域、先前技術、內容、實施方式及圖式簡單說明) 【發明所屬之技術領域】 本發明係有關一種熱交換器及其製造方法，係使用於作 爲例如冰箱或冷藏展示櫃等冷卻裝置之蒸發器。 在本說明書中，在第3圖及第7圖中以箭頭X所示之方 向係設爲前、與其相反側則設爲後。此外，即使在第1圖、 第4圖及第5圖中亦是以此種前後方向作爲基準。再者， 爲將各圖面之上下稱爲上下，將第1圖、第3圖、以及第 7圖之左右設爲左右。 【先前技術】 習知，係使用於第7圖所示之物來作爲冰箱或冷藏展示 櫃等冷卻裝置之蒸發器。在第7圖中，習知之蒸發器（30) 係具備有：2個散熱片群（3 2 )，係由呈並列狀的配置在左 右方向之多數個板狀散熱器（3 1 )所形成，且於上下方向設 置呈隔有一間隔；多數個直管（3 3 )，將前後方配置呈隔有 一間隔，且分別貫通上下兩散熱片群（3 2 )之全數板狀散熱 器（31);多數個U型彎管（34)，係連接相鄰接之各直管 (3 3 )，以使冷煤依次流通全數直管（3 3 )內。 此種蒸發器（3 0 )係爲藉由下述方法所製造。亦即’首先 準備多根直管（3 3 )、以及將多數貫通孔隔有一間隔所形成 之板狀散熱器（3 1 )’同時，準備有將擴管用球安裝至線纜 一端之擴管具。並且，在將前述直管（3 3 )分別通過全數板 0301343 狀散熱器（3 1 )之貫通孔後，將擴管具用線纜由一端側通過 直管’同時，將線纜由另一端側拉伸、藉由將擴管用球通 過直管（3 3 )內而使直管（3 3 )擴管，且將全數板狀散熱器（3 1 ) 固定在直管周圍。接著，藉由熔接直管（3 3 )之端部與U型 彎管（34)之端部，而將全數直管（33)藉由U型彎管（34)連 接。如此，以製造出蒸發器（3 0 )。 不過’近年來，在冰箱或冷藏展示櫃等冷卻裝置中，雖 有探討使用對於臭氧層破壞或地球溫室效應之影響較少的 碳氫化合物系冷煤來取代習知之氟氯烷（freon)系冷煤，不 過’因碳氫化合物系冷煤係具有可燃性，故而必須極力抑 制冷煤的洩漏。 然而，在上述習知之蒸發器（30)中，直管（33)與U型彎 管（3 4 )係被熔接，因此具有冷煤自其熔接接合處洩漏之虞。 在此，作爲用以解決此種問題之蒸發器，係考慮有將以 Z型曲線狀管與散熱片群所構成之附散熱片之Z型曲線狀 管，在未設有散熱片群之多處上藉由彎曲而將整體形成爲 蛇行狀之物。該散熱片群係構成如下，即，在Z型曲線狀 管之長度方向上隔有間隔、設有多數個，並且跨越Z型曲 線狀管之2個直管部、而由被固定在兩直管部之多數並列 狀板狀散熱器所形成。 此種蒸發器之製造方法係如下述。亦即，首先準備Z型 曲線狀管、以及2個貫通孔爲隔有間隔而形成之多數板狀 散熱器，同時，準備有在按壓桿前端安裝有擴管用心軸 (m a n d 1· e 1 )之擴管具。並且，藉由將Z型曲線狀管之兩直管 _ 8 - 0301343 部分別通過全數板狀散熱器之兩貫通孔，而將由多數並列 狀板狀散熱器所形成之非固定散熱片群以多數設在於直管 部之長度方向隔有一間隔。接著，將擴管具之擴管用心軸 由z型曲線狀管之兩端開口壓入至直管部內而使直管部擴 管，將各散熱片群之板狀散熱器固定在z型曲線狀管之直 管部周圍，藉以製造附散熱片之z型曲線狀管。之後’藉 由將附散熱片之z型曲線狀管於未設有散熱片群之多處上 進行彎曲，而將整體形成爲蛇行狀。如此，而製造出蒸發 器。 在藉由此種方法所製造之蒸發器中，因在附散熱片之Z 型曲線狀管之Z型曲線狀管方面並未存在有接合處，因此 不會發生如第7圖所示之蒸發器（3 0 )的冷煤洩漏，不過， 板狀散熱器係僅有跨越2個直管部之大小’故而藉由增大 傳熱面積所達之冷卻效率提昇效果較少。 本發明之目的係爲解決上述問題，提供一種熱交換器， 係在已使用有冷卻裝置之蒸發器的情況下，可防止冷煤洩 漏的同時可使冷卻性能提昇。 【發明內容】 本發明之熱交換器係爲，具備有：蛇行管，所具有之直 管部係爲，藉由彎曲未有熔接接合處之1根管子所形成、 且在前後方向隔一間隔，而呈平行設置之3處以上之直管 部；多數板狀散熱器，係被固定在直管部之周圍。 若藉由本發明之熱交換器，則蛇行管爲以彎曲未有熔接 接合處之1根管子所形成，因此在將此種熱交換器用於冷 - 9 - 200301343 卻裝置之蒸發器的情況下，可防止冷煤的洩漏。從而，可 使用對於臭氧層破壞或地球溫室效應之影響較少的碳氫化 合物系冷煤。此外，因具備有相互設成平行之具有3處以 上直管部之蛇行管、以及被固定在直管部周圍之多數板狀 散熱器，因而可增加板狀散熱器之數目，增大傳熱面積、 提昇熱交換效率，而在使用於例如冷卻裝置之蒸發器的情 況下爲使冷卻效率提昇。 在本發明之熱交換器中，係具備有：第1散熱片群，係 由跨越蛇行管之相鄰接之2個直管部、且呈並列狀固定在 兩直管部之多數板狀散熱器所形成；第2散熱片群，係呈 並列狀的被固定在蛇行管之殘餘的各直管部，且由多數板 狀散熱器所形成。在此情況下，係可增加板狀散熱器之數 目，增大傳熱面積、提昇熱交換效率，而在使用於例如冷 卻裝置之蒸發器的情況下爲使冷卻效率提昇。 在本發明之熱交換器中，於蛇行管之內周面上，在其長 度方向延伸之內部散熱片係於周方向隔有間隔而形成爲一 體狀。在此情況下，係使熱交換器之熱交換性能提昇。 在本發明之熱交換器中，板狀散熱器係被固定在藉由使 用流體而擴管之蛇行管的直管部上。在此情況下，即使是 以在蛇行管之內周面中增大傳熱面積爲目的，而形成有較 爲突出高度之內部散熱片，於擴管時亦不會使內部散熱片 崩潰，而可獲得所期望之冷卻性能（熱交換性能）。 在本發明之熱交換器中，由蛇行管之內周面形成突出高 度相異之高低2種種類的內部散熱片’係呈交互狀的設於 - 10- 周方向上，較高之內部散熱片之突出高度係爲0.7〜 1 . 7mm，較低之內部散熱片之突出高度係爲〇 . 4〜1 . 2mm。 在此情況下，此種熱交換器爲形成在熱交換性能提昇效果 上極爲優越之物。 在蛇行管之內周面設有高低2種種類之內部散熱片之本 發明的熱交換器中，內部散熱片之節距係形成爲0 . 4〜 1 . 6mm 0 此外，在蛇行管之內周面設有高低2種種類之內部散熱 片之本發明的熱交換器中，蛇行管之外徑係爲6〜1 0mm， 其周壁之厚度係形成爲0.4〜0.8mm。 在本發明之熱交換器中，全數內部散熱器之高度係爲相 等，而來自蛇行管之內周面之內部散熱片的突出高度係形 成爲0 . 7〜1 . 2mm。在此情況下，此種熱交換器爲形成在熱 交換性能提昇效果上極爲優越之物。 在全數內部散熱片之高度爲相等之本發明之熱交換器 中，內部散熱片之節距係形成爲0 . 4〜1 . 6mm。 在全數內部散熱片之高度爲相等之本發明之熱交換器 中，蛇行管之外徑係爲6〜10mm，其周壁之厚度係形成爲〇 . 4 〜0 · 8mm 〇 在本發明之熱交換器中，構成第2散熱片群之板狀散熱 器之前後方向的長度係形成爲構成第1散熱片群之板狀散 熱器之前後方向長度之略一半値。 在本發明之熱交換器中，第1散熱片群之節距係與第2 散熱片群之節距形成相異。例如，將第2散熱片群之節距 -11- f 200301343 形成爲大於第l散熱片群之節距。 藉由本發明所達成之其他熱交換器係爲，由附散熱片蛇 行管所形成，該附散熱片蛇行管係構成如下：蛇行管，所 具有之直管部係爲，藉由彎曲未有熔接接合處之1根管子 所形成、且在前後方向隔一間隔，而呈平行設置之3處以 上之直管部；第1散熱片群，係跨越蛇行管之相鄰接之2 個直管部，且由呈並列狀固定在兩直管部之多數板狀散熱 器所形成，同時在直管部之長度方向係隔有間隔，而設有 多數之第1散熱片群；第2散熱片群，係呈並列狀的被固 定在蛇行管之殘餘的各直管部，且由多數板狀散熱器所形 成’同時在有關於直管部之長度方向係形成爲與第1散熱 片群相同位置般地在直管部之長度方向係隔有間隔，而設 有多數之第2散熱片群；附散熱片蛇行管係爲，於全數直 管部中相鄰接之第1散熱片群間與第2散熱片群間之中， 各個第1散熱片群與各個第2散熱片群係以形成如上下重 疊彎曲狀，而相鄰接之第1散熱片群間與第2散熱片群間 之上述間隔係形成爲彎曲附散熱片蛇行管的直管部所呈之 長度。 藉由本發明所達成之其他熱交換器係爲，蛇行管爲藉由 彎曲未有熔接接合處之1根管子所形成，因此在將此種熱 父換器用於冷卻裝置之蒸發器的情況下，可防止冷煤的洩 漏。從而，可使用對於臭氧層破壞或地球溫室效應之影響 較少的碳氫化合物系冷煤。此外，因具備有跨越蛇行管之 相鄰接之2個直管部、且由呈並列狀固定在兩直管部之多 - 12- 0301543 數板狀散熱器所形成之第1散熱片群，以及呈並列狀的被 固定在蛇行管之殘餘的各直管部、且由多數板狀散熱器所 形成之第2散熱片群，故而可增加板狀散熱器之數目，增 大傳熱面積、提昇熱交換效率，而在使用於例如冷卻裝置 之蒸發器的情況下爲使冷卻效率提昇。特別是第1散熱片 群及第2散熱片群係設呈上下2段，因此藉由傳熱面積之 增大，而更加提昇熱交換效率、例如用於冷卻裝置之蒸發 器之情況的冷卻效率。 φ 在本發明之其他熱交換器中，於蛇行管之內周面上，在 其長度方向延伸之內部散熱片係於周方向隔有間隔而形成 爲一體狀。在此情況下，係使熱交換器之熱交換性能提昇。 在本發明之其他熱交換器中，板狀散熱器係被固定在藉 由使用流體而擴管之蛇行管的直管部上。在此情況下，即 使是以在蛇行管之內周面中增大傳熱面積爲目的，而形成 有較爲突出高度之內部散熱片，於擴管時亦不會使內部散 熱片崩潰，而可獲得所期望之冷卻性能（熱交換性能）。 · 在本發明之其他熱交換器中，由蛇行管之內周面形成突 出高度相異之高低2種種類的內部散熱片，係呈交互狀的 設於周方向上，較高之內部散熱片之突出高度係爲0.7〜 1 . 7mm，較低之內部散熱片之突出高度係爲〇.4〜1 .2_。 在此情況下，此種熱交換器爲形成在熱交換性能提昇效果 上極爲優越之物。 在蛇行管之內周面設有高低2種種類之內部散熱片之本 發明的其他熱交換器中，內部散熱片之節距係形成爲〇 . 4 - 1 3 - 200301543 〜1 · 6ιώιώ 0 此外，在蛇行管之內周面設有' ®低1 2種種類之內@散熱 片之本發明的其他熱交換器中’蛇行管之外徑係爲6〜 1 0 m m ’其周壁之厚度係形成爲〇.4〜0·8ιώιώ。 在本發明之其他熱交換器中’全數內部散熱器之高度係 爲相等，而來自蛇行管之內周面之內部散熱片的突出高度 係形成爲〇 . 7〜1 · 2mm °在此情況下’此種熱交換器爲形成 在熱交換性能提昇效果上極爲優越之物。 在全數內部散熱片之高度爲相等之本發明之其他熱交換 器中，內部散熱片之節距係形成爲0 · 4〜1 . 6 m m。 在全數內部散熱片之高度爲相等之本發明之其他熱交換 器中，蛇行管之外徑係爲6〜ΙΟίΏΙΏ’其周壁之厚度係形成 爲 0 · 4 〜0 . 8mm 0 在本發明之其他熱交換器中，構成第2散熱片群之板狀 散熱器之前後方向的長度係形成爲構成第1散熱片群之板 狀散熱器之前後方向長度之略一半値。 在本發明之其他熱交換器中，第1散熱片群之節距係與 第2散熱片群之節距形成相異。例如，將第2散熱片群之 節距形成爲大於第1散熱片群之節距。 藉由本發明所達成之冷卻裝置係爲，所具備之冷凍循環 爲具有壓縮機、冷凝器、以及蒸發器，蒸發器係由上述任 一項之熱交換器所形成，爲使用碳氫化合物系冷煤以作爲 冷煤’同時，冷煤循環量係形成爲1〜9 k g / h。 藉由本發明所達成之熱交換器製造方法係爲，在製造申 -14- 請專利範圍第2項所述之熱交換器之方法中，係準備藉由 彎曲未有熔接接合處之1根管子所形成Z型曲線狀管、以 及2個貫通孔爲在前後方向隔一間隔所形成之多數板狀散 熱器，藉由將Z型曲線狀管分別通過全數板狀散熱器之貫 通孔，而將由多數並列狀板狀散熱器所形成之非固定散熱 片群以所定數目設於將直管部彎曲在直管部之長度方向、 且隔有該長度之間隔，而固定呈擴管Z型曲線狀管、以使 各板狀散熱器跨越兩直管部，藉以獲得形成第2散熱片群 之被分割散熱片群、以及具有第1散熱片群之附散熱片之 Z型曲線狀管，且將構成全數被分割散熱片群之板狀散熱 器分割成固定在一方之直管部的部分、以及固定在另一方 之直管部的部分以形成第2散熱片群，而包含有將附散熱 片Z型曲線狀管之兩直管部朝前後方向外方彎曲。 藉由本發明所達成之熱交換器製造方法，係可較簡單的 製造出達到上述效果之申請專利範圍第2項之熱交換器。 藉由本發明所達成之熱交換器製造方法係爲，在製造申 請專利範圍第1 4項所述之熱交換器之方法中，係準備藉由 彎曲未有熔接接合處之1根管子所形成Z型曲線狀管、以 及2個貫通孔爲在前後方向隔一間隔所形成之多數板狀散 熱器，藉由將Z型曲線狀管分別通過全數板狀散熱器之貫 通孔，而將由多數並列狀板狀散熱器所形成之非固定散熱 片群以所定數目設於將直管部彎曲在直管部之長度方向、 且隔有該長度之間隔，將該所定數目設成，設於Z型曲線 狀管之彎曲部側、且形成第1散熱片群爲2處以上之非固 - 15- f 200301343 定散熱片群之數目的n倍（n爲2以上之整數），而固定呈 擴管Ζ型曲線狀管、以使各板狀散熱器跨越兩直管部，藉 以獲得形成第2散熱片群之被分割散熱片群、以及具有第 1散熱片群之附散熱片之ζ型曲線狀管’且將構成全數被 分割散熱片群之板狀散熱器分割成固定夸一方之直管部的 部分、以及固定在另一方之直管部的部分以形成第2散熱 片群，包含有藉由將附散熱片Ζ型曲線狀管之兩直管部朝 前後方向外方彎曲所形成之附散熱片蛇行管。 藉由本發明所達成之熱交換器製造方法’係可較簡單的 製造出達到上述效果之申請專利範圍第1 4項之熱交換器。 在本發明之2種熱交換器之製造方法中’於Ζ型曲線狀 管之內周面上、沿其長度方向延伸之內部散熱片’係爲在 周方向隔有間隔而形成爲一體。 在本發明之2種熱交換器之製造方法中，Ζ型曲線狀管 之擴管爲使用流體來進行。 在本發明之2種熱交換器之製造方法中’由Ζ型曲線狀 管之內周面形成突出高度相異之高低2種種類自勺內部散熱 片，係呈交互狀的設於周方向上，較高之內部散熱片之突 出高度係爲0 . 7〜1 · 7mm，較低之內部散熱片之突出高度係 爲 0·4 〜1 ·2mm 〇 在Z型曲線狀管之內周面設有高低2種種類之內部散熱 片之本發明的熱交換器之製造方法中’內部散熱片之節距 係形成爲0 . 4〜1 . 6 m m。 在Z型曲線狀管之內周面設有高低2種種類之內部散熱 -16 - 片之本發明的熱交換器之製造方法中，z型曲線狀管之外 徑係爲6〜10 mm，其周壁之厚度係形成爲0.4〜0.8 mm。 在本發明之2種熱交換器之製造方法中，全數內部散熱 器之高度係爲相等，而來自Z型曲線狀管之內周面之內部 散熱片的突出高度係形成爲〇 . 7〜1 · 2mm。 在全數內部散熱片之高度爲相等之本發明之2種熱交換 器之製造方法中，內部散熱片之節距係形成爲 〇 . 4〜 1 . 6mm 0 在全數內部散熱片之高度爲相等之本發明之2種熱交換 器之製造方法中，Z型曲線狀管之外徑係爲6〜1 0mm ’其周 壁之厚度係形成爲〇·4〜〇.8mm。 在本發明之2種熱交換器之製造方法中，形成第2散熱 片群、構成被分割散熱片群之板狀散熱器係爲’將2種散 熱片形成部與兩散熱片形成部藉由連結部而一體形成爲可 分割狀。在此情況下，除了可將Z型曲線狀管在通過板狀 散熱器之貫通孔時可容易地進行安裝，同時，可簡單的進 行作爲後續工程中之板狀散熱器之分割。 在本發明之2種熱交換器之製造方法中，係將構成第1 散熱片群之板狀散熱器、以及以形成第2散熱片群之被分 割散熱片群所構成之板狀散熱器形成爲相同形狀’在構成 被分割散熱片群之板狀散熱器中，上下兩側緣中之至少一 方的前後方向之中央部上係形成有v字型之刻痕’同時在 與關於前後方向刻痕相合之位置上，形成有不至干涉刻痕 而於上下方向延伸之裂縫。在此情況下，在將附裂縫之板 -17- 狀散熱器進行衝壓成型時，在用以將另一方板狀散熱器進 行衝壓成型所用之衝壓模具上，亦可使用可將切痕形成部 及裂縫形成部呈拆卸自如狀之物，而可使用1種種類之衝 壓模具來成型2種種類之板狀散熱器。其結果，係可降低 板狀散熱器之製造成本。此外，係將V字型刻痕形成於構 成被分割散熱片群之板狀散熱片中之上下兩側緣中之至少 一方之前後方向的中央部，同時，在有關前後方向而與刻 痕相合之位置上，因形成有不至干涉刻痕而於上下方向延 伸之裂縫，故可簡單的進行此種板狀散熱器之分割。 在本發明之2種熱交換器之製造方法中，分割被分割散 熱片群而形成第2散熱片群後，可切斷在附散熱片Z型曲 線狀管中具有所定數目之第2散熱片群的直管部。 【實施方式】 以下，參照圖面說明本發明之實施例。在此實施例中， 係爲將本發明之熱交換器適用於冷卻裝置之蒸發器。此外， 在以下說明中，所謂的「鋁」之用語係指純鋁之外包含有 鋁合金之物。 第1圖及第2圖所示係用以形成蒸發器之附散熱片蛇行 管’第3圖係揭示蒸發器。此外，第4圖所示係用以形成 附散熱片蛇行管之附散熱片Z型曲線狀管，第5圖係揭示 板狀散熱器。 在第1圖及第2圖中，附散熱片蛇行管（1 )係具備有：鋁 製蛇行管（2 )，爲在前後方向隔有間隔而設有3處以上（在 此爲4處）直管部（2 a );多數（在此爲2個）第1散熱片群 -18- 2υύ301-^3 (2 )，係於蛇行管（2 )中、中央部之相鄰接的2個直管部（2 a ) 之長度方向上隔有間隔所設置；多數（在此爲2個）第2散 熱片群（4 )，係於蛇行管（2 )之前後兩端之直管部（2 a )上， 分別於長度方向隔有間隔所設置。兩第1散熱片群（3 )間及 兩第2散熱片群（4 )間之間隔係爲，將直管部（2 a )形成爲使 各個第1散熱片群（3)與各個第2散熱片群（4)呈上下重疊 狀折返彎曲的長度。 蛇行管（2 )係藉由彎曲未有熔接接合處之1根管子所形 成，在其內周面上，朝其長度方向延伸、且突出高度相異 之高低2種種類的內部散熱片（20 )( 2 1 )，係形成在周方向 上隔有間隔、且於周方向上隔有間隔的成交互狀而形成爲 一體狀。內部散熱片（20 )( 2 1 )係爲朝向蛇行管（2 )之中心而 突出。而由較高之內部散熱片（20)之蛇行管（2)之內周面之 突出高度（hi)係爲0.7〜1.7mni，較低之內部散熱片（21)之 突出高度係爲0.4〜1.2 mm。此外，內部散熱片（20)(21)之 節距（P )係形成爲〇 . 4〜1 . 6mm。在此，內部散熱片（20 ) ( 2 1 ) 之節距（P )係爲，在橫剖面中，爲連結蛇行管（2 )之中心線、 以及相鄰接之2個內部散熱片（20 )( 2 1 )之厚度中心的2直 線（L 1 ) ( L2 )間之蛇行管（2 )之外周面上之周方向之距離。此 外’蛇行管（2)之外徑係形成爲6〜10mm、其周壁之厚度爲 形成0.4〜〇.8mm。 桌1散熱片群（3)係由跨越2個直管部（2a)、且固定在兩 直管部（2 a )之多數並列狀鋁製板狀散熱器（5 )所形成。板狀 散熱器（5 )係爲在前後方向上較長之長方形。以下，將構成 第1散熱片群（3 )之板狀散熱器（5 )稱爲第1板狀散熱器。 第2散熱片群（4)係由固定在各直管部（2a)之多數鋁製板狀 散熱器（6 )所形成，在有關於直管部（2 a )之長度方向係形成 爲與第1散熱片群（3)呈相同位置。第2散熱片群（4)之板 狀散熱器（6 )之前後方向長度係等於第1板狀散熱器之長度 之1 / 2，或是形成僅短於後述切痕（1 2 )與裂縫（1 3 )之部分。 以下，將構成第2散熱片群（4 )之板狀散熱器（6 )稱爲第2 板狀散熱器。第1散熱片群（3 )與第2散熱片群（4 )之散熱 片節距係有形成爲相異的情況，而以第2散熱片群（4 )之散 熱片節距爲大於第1散熱片群（3 )之散熱片節距者爲佳。 在第1散熱片（5 )方面，於前後方向隔有間隔、形成有2 個貫通孔（5 a )，蛇行管（2 )之中央部的2個直管部（2 a )係分 別通過全數第1板狀散熱器（5 )之貫通孔（5 a )，藉由擴管兩 直管部（2a)而使第1板狀散熱器（5)固定在兩直管部（2a)之 周圍。第2板狀散熱器（6 )中係形成有1個貫通孔，蛇行管 (2 )之前後兩端的直管部（2 a )係分別通過全數第2板狀散熱 器（6 )之貫通孔，藉由擴管兩直管部（2 a )而使第2板狀散熱 器（6 )固定在直管部（2 a )之周圍。此外，亦可維持附散熱片 蛇行管（1 )之狀態來作爲蒸發器所使用。 接著如第3圖所示，附散熱片蛇行管（1 )係爲，於蛇行管 (2 )之全數直管部（2 a )中相鄰接之第1散熱片群（3 )間與第 2散熱片群（4)之間中，各個第1散熱片群（3)與各個第2 散熱片群（4 )係以形成如上下重疊彎曲狀，藉此而形成蒸發 器（E)。亦即，在此種蒸發器（E)中，2個第1散熱片群（3) - 2 0 - 係於上下方向呈積層狀配置的同時，在該等第1散熱片群（3 ) 之前後兩側中，分別使2個第2散熱片群（4 )於上下方向呈 積層狀的配置，在各第1散熱片群（3 )之第1板狀散熱器（5 ) 上使前後2根直管部（2 b )貫通，且於各第2散熱片群（4 )之 第2板狀散熱器（6 )上使1根直管部（2b )貫通。並且，在較 散熱片群（3 )( 4 )更爲左方上，相關於前後方向而於相同位 置上，上下直管部（2b)係藉由形成爲一體之彎曲部（2c)所 連接。此外，在散熱片群（3 )( 4 )之右方中，於上側直管部（2b ) 中之前後兩側之2根係分別形成爲一體而藉由彎曲部（2d ) 所連接，同時，於下側直管部（2b )中之中央2根係與其形 成爲一體而藉由彎曲部（2 e )所連接。 其次，針對蒸發器之製造方法進行說明。 首先，製造於第4圖所示之附散熱片Z型曲線狀管（Η)。 亦即，準備有（參照第5圖）：Ζ型曲線狀管（1 0 )，藉由 彎曲未有熔接接合處之1根鋁製管子所形成；多數鋁製之 第1板狀散熱器（5 )，係於前後方向隔有間隔、且形成2個 貫通孔（5 a );多數鋁製之板狀散熱器（1 1 )，係於前後方向 隔有間隔、且形成2個貫通孔（1 1 a )。 在Z型曲線狀管（1 0 )之內周面上，於其長度方向延伸、 且突出高度相異之高低2種種類的內部散熱片（20 )( 2 1 )， 係於周方向上隔有間隔而呈交互狀的一體形成。內部散熱 片（2 0 )( 2 1 )係如同先前參照第2圖所示之物。 如第5圖之（a )、（ b )所示，該等板狀散熱器（5 ) ( 1 1 )係爲 在前後方向上較長之長方形，在一方之板狀散熱器（11)之 -21- 上下兩側緣部之前後方向之中央部上係形成有v字型之刻 痕（1 2 )’同時在兩刻痕（1 2 )間形成有於板狀散熱器（1 1 )之 寬度方向（上下方向）延伸之裂縫（1 3 )。貫通孔（1 1 a )係被形 成在裂縫（1 3 )之前後兩側。兩刻痕（1 2 )與兩裂縫（1 3 )之間 的間隔係以設呈0 · 1〜0 · 4mm程度者爲佳。以下，將具有刻 痕（1 2 )與裂縫（1 3 )之板狀散熱器（1 1 )稱之爲附裂縫之板狀 散熱器。附裂縫之板狀散熱器（1 1 )係爲，在用以將第1板 狀散熱器（5 )進行衝壓成型所用之衝壓模具上，將切痕形成 部及裂縫形成部呈拆卸自如狀以衝壓所形成。在此，藉由 形成刻痕（1 2 )與裂縫（1 3 )，附裂縫之板狀散熱器（1 1 )係由 被設在前後2個散熱片形成部（1 5 )，以及刻痕（1 2 )與裂縫 (1 3 )之間、且一體連結至可分割兩散熱片形成部（1 5 )的連 結部（1 6 )所形成。 並且，藉由將Z型曲線狀管（10)之兩直管部（l〇a)通過全 部的板狀散熱器（5 ) ( 1 1 )之兩貫通孔（5 a ) ( 1 1 a )，而將由多 數板狀散熱器（5 )( 1 1 )所形成之非固定散熱片群於直管部 (2 a )之長度方向上隔有間隔、且設置多數（在此爲4個）。 此時，Z型曲線狀管（1 0 )之彎曲部（1 Ob )側之2個非固定散 熱片群係爲由第1板狀散熱器（5 )所形成之物’而形成有附 散熱片蛇行管（1 )之第1散熱片群（3 )。此外’ Z型曲線狀 管（1 0 )之兩端開口側之2個非固定散熱片群係爲由附裂縫 之板狀散熱器（1 1 )所形成之物，而形成有附散熱片蛇行管（1 ) 之第2散熱片群（4 )。形成第1散熱片群（3 )之非固定散熱 片群間之間隔係爲，形成爲如同重疊各個第1散熱片群（3 ) -22- 而彎曲兩直管部（10a)的長度’且成爲與形成第2散熱片群 (4 )之非固定散熱片群間之間隔相等。此外’非固定散熱片 群之總數係爲形成第1散熱片群（4 )之非固定散熱片群之數 目的η倍（11爲2以上之整數）。 接著，在此狀態下將水、油、空氣等壓力流體導入至Ζ 型曲線狀管（1 〇)內而使其擴管，藉由將各非固定散熱片群 之第1板狀散熱器（5 )與附裂縫之板狀散熱器（11 )固定在Ζ 型曲線狀管（10)之兩直管部UOa)周圍’而製造出具有形成 第2散熱片群（4 )之2個被分割散熱片群（1 4 )、以及2個第 1散熱片群（3 )的附散熱片Z型曲線狀管（Η )(參照第4圖）。 此外，Ζ型曲線狀管（1 〇 )之擴管亦可如下述所進行，即， 在按壓桿之前端準備已安裝有擴管用心軸之擴管具’而由 Ζ型曲線狀管（1 〇 )將擴管具之擴管用心軸按壓至直管部（2 a ) 內來進行。 之後，使用附散熱片Z型曲線狀管（Η )、製造出附散熱片 蛇行管（1 )。亦即，首先，將構成Ζ型曲線狀管（1 〇 )之2個 被分割散熱片群（1 4 )的附裂縫之板狀散熱器（1 1 )，形成爲 在刻痕（1 2 )與裂縫（1 3 )之間的連結部（1 6 )中，分割呈固定 在一方之直管部（l〇a)的部分以及固定在另一方之直管部 (1 0 a )的部分而形成第2散熱片群（4 )。附裂縫之板狀散熱 器（1 1 )之分割係爲，一面將楔子壓入兩刻痕（1 2 )中、一面 藉由在前後方向進行拉伸而進行。接著，將附散熱片Z型 曲線狀管（Η )之Z型曲線狀管（1 0 )的兩直管部（丨〇 a )，由ζ 型曲線狀管（1 0 )之彎曲部側第2個第1散熱片群（3 )與第3 -23- 個第2散熱片群（4 )之間而分別朝前後方向外方彎曲（參照 第1圖之鏈線）。如此，在蛇行管（2 )中，所製造出之附散 熱片蛇行管（1 )係具備有：多數第1散熱片群（3 )’係於中 央部相鄰接之2個直管部（2 a )之長度方向上隔有間隔而設 置者；以及多數第2散熱片群（4 )，係於蛇行管（2 )之前後 兩端直管部（2 a )之長度方向上隔有間隔而設置者。 最後，附散熱片蛇行管（1 )係爲，於全數直管部（2a)中相 鄰接之第1散熱片群（3 )間與第2散熱片群（4 )之間的部份 中，各個第〗散熱片群（3 )與各個第2散熱片群（4 )係以形 成如上下重疊彎曲狀，藉此而形成蒸發器（E )(參照第3圖 之鏈線）。 蒸發器（E )所具備之冷凍循環爲具有壓縮機、冷凝器、以 及蒸發器，使用有採用以碳氫化合物系冷煤作爲冷煤之冰 箱、或是冷藏展示櫃等冷卻裝置之蒸發器。在此種冷卻裝 置中，冷煤循環量係形成爲1〜9kg/h之低循環量。 在上述實施例中，在用以形成蒸發器（E )之附散熱器蛇行 管（1 )中之蛇行管（2 )的直管部（2 a )之數目爲4個，因此， 在附散熱器Z型曲線狀管（Η )中，由附裂縫之板狀散熱器（1 1 ) 所形成之被分割散熱片群（1 4 )之數目係與第1散熱片群（3 ) 之數目相等，不過並不僅限於此，直管部（2 a )之數目係可 爲2 η ( η爲2以上之整數）之任意數目。在此情況下，於附 散熱器Ζ型曲線狀管（Η )中，爲將由附裂縫之板狀散熱器（1 1 ) 所形成之被分割散熱片群（1 4 )之數目設爲第1散熱片群（3 ) 之數目的（η - 1 )倍。此外，在附散熱器Ζ型曲線狀管（Η )中， -24 - 藉由將Z型曲線狀管（1 ο )之兩直管部（1 0 a )呈蛇行狀的朝前 後方向外方彎曲，以形成附散熱片蛇行管。此外，在附散 熱片蛇行管（1 )中之蛇行管（2 )之直管部（2 a )的數目爲具有 形成爲3以上之奇數的情況、亦即爲形成2n - 1 ( η爲2以上 之整數）之情況，不過，在此情況下，於分割被分割散熱片 群（1 4 )之附裂縫之板狀散熱器（1丨）後，亦可將Ζ型曲線狀 管（10)之一方直管部（l〇a)截斷至具有由其開口端到與第1 散熱片群（3)相同數目之第2散熱片群（4)爲止的長度部 分。 此外’在上述實施例中，蒸發器之第1散熱片群（3 )與第 2散熱片群（4 )係分別設於上下2段，不過並不僅限定於此， 亦可設呈上下3段以上。在此情況下，於附散熱器蛇行管（1 ) 中之第1散熱片群（3)與第2散熱片群（4)之數目設呈3以 上。此外，第1散熱片群（3 )與第2散熱片群（4 )之數目亦 可爲1。 再者’在上述實施例與其他實施例中，在應分割之板狀 散熱器中並無~定之必要來形成裂縫（1 3 )與刻痕（1 2 )。 此外’本發明之熱交換器係爲，亦可使用於冷卻裝置之 蒸發器以外之物。 第6圖所示係用於形成蒸發器之附散熱片蛇行管（1 )之蛇 行管（2 )之變形例。 在第6圖中，於蛇行管（2)之內周面上，沿其長度方向延 伸、且突出高度相等之多數內部散熱片（22)係爲，在周方 向隔有間隔而形成爲一體。來自內部散熱片（2 2 )之蛇行管（2 ) -25- 之內13面的关出筒度（h3)係爲0.7〜1.2mm。此外，內部散 熱片（22 )之節距（p )係爲〇 . 4〜i 6mm。在此，內部部散熱 片（22 )之節距（P )係與上述相同。此外，蛇行管（2 )之外徑 係爲6〜10mm’其周壁之壁厚爲形成Q.4〜0.8mni。 【發明之效果】 〔產業上利用之可能性〕 本發明之熱交換器係作爲冰箱、或是冷藏展示櫃等冷卻 裝置之蒸發器所使用，特別爲適用於使用有碳氫化合物系 _ 冷煤之冷卻裝置之蒸發器。 【圖式簡單說明】 第1圖所示係用以形成適用於本發明之蒸發器的附散熱 片蛇行管之立體圖。 第2圖所示係沿第1圖之I I - I I線剖面之擴大剖面圖。 第3圖所示係適用於本發明之蒸發器之立體圖。 第4圖所示係用以形成附散熱片蛇行管之附散熱片Z型 曲線狀管之立體圖。 · 第5圖之（a )、（ b )所示係2種種類之板狀散熱器之正面圖。 第6圖所示係附散熱片蛇行管之其他具體例’爲相當於 第2圖之剖面圖。 第7圖所示係習知蒸發器之立體圖。 【主要部分之代表符號說明】 1、2 :蛇行管、附散熱片蛇行管 1 〇、H : Z型曲線狀管 1 2 :刻痕 - 2 6 - 0301543 1 3 :裂縫 2 0、2 1 :內部散熱片 2 a、1 0 a :直管部 3 :第1散熱片群 3 0 :蒸發器 32 :散熱片群 33 :直管 3 4 : U型彎管 4 :第2散熱片群 5 a :貫通孔 6、5、1 1、31 :板狀散熱器 E :蒸發器 hi、h2 :突出高度 L1、L 2 :直線Γ 200301343 Description of the invention (The description of the invention should state: the technical field, prior art, content, embodiments, and drawings of the invention are briefly described.) [Technical field to which the invention belongs] The present invention relates to a heat exchanger and its manufacture The method is an evaporator used as a cooling device such as a refrigerator or a refrigerated display case. In this specification, the directions indicated by arrows X in Figs. 3 and 7 are set to the front, and the opposite sides are set to the rear. In addition, the front-back direction is used as a reference even in FIGS. 1, 4 and 5. In addition, in order to refer to the top and bottom of each drawing as up and down, the left and right sides of the first, third, and seventh figures are set to the left and right. [Prior art] It is conventionally known that it is used as an evaporator of a cooling device such as a refrigerator or a refrigerated display case as shown in FIG. 7. In Fig. 7, the conventional evaporator (30) is provided with two heat sink groups (3 2) formed by a plurality of plate-shaped heat sinks (3 1) arranged side by side in the left-right direction. There are a plurality of plate-shaped radiators (31) arranged at intervals in the up-and-down direction; a plurality of straight tubes (3 3) are arranged at the front and rear and spaced through and penetrate the upper and lower fin groups (3 2) respectively. A plurality of U-shaped elbows (34) are connected to adjacent straight pipes (3 3) adjacent to each other, so that the cold coal flows through all the straight pipes (3 3) in sequence. Such an evaporator (30) is manufactured by the following method. That is, 'first prepare a plurality of straight pipes (3 3) and a plate-shaped heat sink (3 1) formed by separating most of the through holes with a space'. At the same time, prepare an expansion pipe that installs a ball for pipe expansion to one end of the cable. With. In addition, after passing the straight pipe (3 3) through the through holes of the all-board 0301343-like heat sink (3 1), the cable for the pipe expansion tool is passed through the straight pipe from one end side and the cable is routed from the other end. Side stretch, expand the straight tube (3 3) by passing the ball for tube expansion into the straight tube (3 3), and fix all plate radiators (3 1) around the straight tube. Next, all the straight tubes (33) are connected by U-shaped elbows (34) by welding the ends of the straight tubes (3 3) and the ends of the U-shaped elbows (34). In this way, an evaporator (30) is manufactured. However, in recent years, in cooling devices such as refrigerators and refrigerated display cabinets, the use of hydrocarbon-based cold coal that has little effect on the ozone layer destruction or the global greenhouse effect has been explored to replace the conventional freon-based refrigerants. Coal, but because of the flammability of hydrocarbon-based cold coals, it is necessary to minimize the leakage of cold coals. However, in the conventional evaporator (30), the straight pipe (33) and the U-shaped elbow pipe (3 4) are welded, so there is a possibility that cold coal may leak from the welded joint. Here, as an evaporator for solving such a problem, a Z-shaped curved tube with a fin composed of a Z-shaped curved tube and a fin group is considered. The whole is formed into a meandering shape by bending. This fin group is structured as follows: a plurality of Z-shaped curved tubes are spaced apart from each other in the lengthwise direction of the Z-shaped curved tubes, and the two straight tube sections of the Z-shaped curved tubes are fixed to two straight tubes. Most of the tube portions are formed by parallel plate heat sinks. The manufacturing method of such an evaporator is as follows. That is, firstly, a Z-shaped curved tube and a plurality of plate-shaped radiators formed with two through holes spaced apart are prepared, and a tube expansion mandrel (mand 1 · e 1) is prepared at the front end of the pressing rod. The pipe expansion. In addition, by passing the two straight tubes _ 8-0301343 of the Z-shaped curved tube through the two through holes of the full plate radiator, the non-fixed heat sink group formed by the majority of the parallel plate radiators is mostly It is provided at intervals in the longitudinal direction of the straight pipe portion. Next, the mandrel for pipe expansion of the pipe expansion tool is pushed into the straight pipe portion from the two ends of the z-shaped curved pipe to expand the straight pipe portion, and the plate radiators of each fin group are fixed to the z-shaped curve. Around the straight tube portion of the tube, a z-shaped curved tube with a fin is manufactured. After that, the z-shaped curved tube with fins is bent at a plurality of places where no fin group is provided, and the whole is formed into a meandering shape. In this way, an evaporator is manufactured. In the evaporator manufactured by this method, since there is no joint in the Z-curved tube of the Z-curved tube with fins, evaporation does not occur as shown in FIG. 7 The cold coal leak of the device (30), but the plate-shaped radiator is only the size spanning two straight pipe sections, so the cooling efficiency improvement effect by increasing the heat transfer area is less. An object of the present invention is to solve the above problems, and to provide a heat exchanger, which can prevent the leakage of cold coal and improve the cooling performance when an evaporator having a cooling device is used. [Summary of the Invention] The heat exchanger of the present invention is provided with a meandering tube, and the straight tube portion is formed by bending a tube without a welded joint and spaced apart in the front-rear direction. At intervals, there are three or more straight pipe sections arranged in parallel; most plate radiators are fixed around the straight pipe sections. According to the heat exchanger of the present invention, the meandering tube is formed by bending a tube without a welded joint. Therefore, when this heat exchanger is used as an evaporator of the cold- 9-200301343 device , Can prevent the leakage of cold coal. Therefore, it is possible to use hydrocarbon-based cold coal which has less influence on the destruction of the ozone layer or the global greenhouse effect. In addition, since it has a meandering tube having three or more straight tube portions arranged in parallel with each other, and a large number of plate radiators fixed around the straight tube portion, the number of plate radiators can be increased to increase heat transfer. The area and heat exchange efficiency are improved, and in the case of an evaporator used in, for example, a cooling device, the cooling efficiency is improved. The heat exchanger of the present invention includes: a first fin group, which is composed of a plurality of plate-shaped heatsinks that are adjacent to two straight tube portions that cross the meandering tube and are fixed in parallel to the two straight tube portions. The second heat sink group is formed in parallel and fixed to the remaining straight tube portions of the meandering tube, and is formed by a large number of plate-shaped heat sinks. In this case, the number of plate-shaped radiators can be increased, the heat transfer area can be increased, and the heat exchange efficiency can be improved. In the case of an evaporator used in a cooling device, for example, the cooling efficiency can be improved. In the heat exchanger of the present invention, the internal fins extending in the longitudinal direction on the inner peripheral surface of the meandering tube are formed in a single body at intervals in the peripheral direction. In this case, the heat exchange performance of the heat exchanger is improved. In the heat exchanger of the present invention, the plate-shaped radiator is fixed to a straight tube portion of a meandering tube which is expanded by using a fluid. In this case, even with the purpose of increasing the heat transfer area in the inner peripheral surface of the meandering tube, an internal fin with a relatively prominent height is formed, and the internal fin will not collapse when the tube is expanded, and The desired cooling performance (heat exchange performance) can be obtained. In the heat exchanger of the present invention, the inner peripheral surface of the meandering tube forms two types of internal fins of different heights with different protruding heights, which are arranged interactively in the direction of the -10-circumferential direction and have higher internal heat dissipation The protruding height of the film is 0. 7 ~ 1. 7mm, the protruding height of the lower internal heat sink is 0. 4 ~ 1. 2mm. In this case, such a heat exchanger is formed to be extremely superior in improving the heat exchange performance. In the heat exchanger of the present invention, the inner peripheral surface of the meandering tube is provided with two types of internal fins, the pitch of the internal fins is formed to 0. 4 ~ 1. 6mm 0 In addition, in the heat exchanger of the present invention in which the inner peripheral surface of the serpentine tube is provided with two types of internal fins, the outer diameter of the serpentine tube is 6 to 10mm, and the thickness of the peripheral wall is formed to 0. . 4 ~ 0. 8mm. In the heat exchanger of the present invention, the heights of all the internal radiators are equal, and the protruding height of the internal fins from the inner peripheral surface of the meandering tube is 0. 7 ~ 1. 2mm. In this case, such a heat exchanger is formed to be extremely superior in improving heat exchange performance. In the heat exchanger of the present invention in which the height of all internal fins is equal, the pitch of the internal fins is formed as 0. 4 ~ 1. 6mm. In the heat exchanger of the present invention in which the height of all internal fins is equal, the outer diameter of the meandering tube is 6 to 10 mm, and the thickness of the peripheral wall is formed as 0. 4 to 0 · 8mm 〇 In the heat exchanger of the present invention, the length of the plate-shaped heat sink constituting the second fin group is formed to be the length of the plate-shaped heat sink constituting the first fin group to the front-rear direction. Slightly half 値. In the heat exchanger of the present invention, the pitch of the first fin group is different from that of the second fin group. For example, the pitch of the second heat sink group -11-f 200301343 is formed to be larger than the pitch of the first heat sink group. Other heat exchangers achieved by the present invention are formed by meandering tubes with fins. The meandering tubes with fins are structured as follows: the meandering tube has a straight tube portion that is not welded by bending Straight pipe sections formed by one pipe at the joint and spaced from each other in the front-to-rear direction by three or more parallel installations; the first heat sink group is two straight pipes that are adjacent to each other across the snake tube And is formed by a plurality of plate-shaped radiators which are fixed in parallel to two straight tube portions, and is spaced apart in the length direction of the straight tube portions, and is provided with a plurality of first heat sink groups; a second heat sink The group is formed in parallel with each straight tube portion fixed to the remaining portion of the meandering tube, and is formed by a plurality of plate-shaped radiators. At the same time, it is formed in the same direction as the first heat sink group in the longitudinal direction of the straight tube portion. Positioned in the lengthwise direction of the straight tube portion, there are a plurality of second fin groups, and the meandering tube system with fins is between the first fin groups adjacent to each other in all the straight tube portions. And the second heat sink group, each first heat sink group and each second heat sink group The heat sink group is formed in a curved shape such that it overlaps up and down, and the distance between the adjacent first heat sink group and the second heat sink group is formed by the length of the straight pipe portion of the meandering tube with the heat sink. . The other heat exchanger achieved by the present invention is that the meandering tube is formed by bending a tube without a welded joint. Therefore, when such a heat exchanger is used as an evaporator of a cooling device, , Can prevent the leakage of cold coal. Therefore, it is possible to use hydrocarbon-based cold coal which has less influence on the destruction of the ozone layer or the global greenhouse effect. In addition, since it has two adjacent straight tube sections that cross the meandering tube and is fixed in parallel to the two straight tube sections, the first heat sink group is formed by several plate-shaped heat sinks. And the second heat sink group formed in parallel and fixed to the remaining straight pipe portions of the meandering tube and formed by most plate heat sinks, the number of plate heat sinks can be increased, the heat transfer area, The heat exchange efficiency is improved, and in the case of an evaporator used in a cooling device, the cooling efficiency is improved. In particular, the first fin group and the second fin group are arranged in two stages, so that the heat transfer area is increased to increase the heat exchange efficiency, such as the cooling efficiency in the case of an evaporator of a cooling device. . φ In another heat exchanger of the present invention, the internal fins extending in the longitudinal direction on the inner peripheral surface of the meandering tube are integrally formed with a gap in the peripheral direction. In this case, the heat exchange performance of the heat exchanger is improved. In another heat exchanger of the present invention, the plate-shaped heat sink is fixed to a straight pipe portion of a meandering pipe which is expanded by using a fluid. In this case, even with the purpose of increasing the heat transfer area in the inner peripheral surface of the meandering tube, an internal fin with a relatively prominent height is formed, and the internal fin will not collapse when the tube is expanded, and The desired cooling performance (heat exchange performance) can be obtained. · In other heat exchangers of the present invention, two types of internal fins with different protruding heights are formed on the inner peripheral surface of the meandering tube. The internal fins are arranged alternately in the circumferential direction and have higher internal fins The protruding height is 0. 7 ~ 1. 7mm, the protruding height of the lower internal heat sink is 0. 4 ~ 1. 2_. In this case, such a heat exchanger is formed to be extremely superior in improving the heat exchange performance. In other heat exchangers of the present invention, the inner peripheral surface of the meandering tube is provided with two types of internal fins, the pitch of the internal fins is formed as 0. 4-1 3-200301543 ～ 1 · 6ιFree Royalty Free 0 In addition, the inner peripheral surface of the serpentine tube is provided with a '® low 1 2 kinds of types @heat sink of other heat exchangers of the present invention' the outer diameter of the serpentine tube The thickness of the peripheral wall is 6 to 10 mm. 4 ~ 0 · 8ι. In the other heat exchangers of the present invention, the height of all the internal radiators is equal, and the protruding height of the internal fins from the inner peripheral surface of the meandering tube is formed as 0. 7 ~ 1 · 2mm ° In this case, this type of heat exchanger is formed to be extremely superior in improving heat exchange performance. In all other heat exchangers of the present invention in which the height of all the internal fins is equal, the pitch of the internal fins is formed as 0.4 · 1. 6 m m. In other heat exchangers of the present invention, where the height of all internal fins is equal, the outer diameter of the meandering tube is 6 ~ ΙΟίΏΙΏ ’, and the thickness of its peripheral wall is formed as 0 · 4 ~ 0. 8mm 0 In another heat exchanger according to the present invention, the length of the plate-shaped heat sink constituting the second fin group is a half of the length of the plate-shaped heat sink constituting the first fin group. . In another heat exchanger of the present invention, the pitch of the first fin group is different from that of the second fin group. For example, the pitch of the second heat sink group is made larger than the pitch of the first heat sink group. The cooling device achieved by the present invention is provided with a refrigeration cycle including a compressor, a condenser, and an evaporator. The evaporator is formed by the heat exchanger of any one of the above, and uses a hydrocarbon-based cooling system. Coal is used as cold coal. At the same time, the amount of cold coal circulation is 1 ~ 9 kg / h. The method for manufacturing a heat exchanger achieved by the present invention is that in the method for manufacturing a heat exchanger described in item 2 of Patent Application No. -14, please prepare a tube by bending an unwelded joint. The Z-shaped curved tube and two through holes formed by the sub-plates are mostly plate radiators formed with an interval in the front-rear direction. By passing the Z-shaped curved tubes through the through holes of all the plate radiators, A fixed number of non-fixed fins formed by a plurality of parallel plate radiators are provided in a predetermined number in a direction where the straight tube portion is bent in the length direction of the straight tube portion, with an interval therebetween, and the tube is fixedly expanded into a Z-shaped curve. To form each plate-shaped heat sink across two straight pipe sections to obtain a divided heat sink group forming a second heat sink group and a Z-shaped curved pipe with a heat sink having a first heat sink group, and The plate-shaped heat sink constituting all the divided fin groups is divided into a portion fixed to one straight pipe portion and a portion fixed to the other straight pipe portion to form a second fin group, and includes a heat sink with additional heat dissipation. Two straight pieces of Z-shaped curved tube Outward bent portion toward the rear direction. With the heat exchanger manufacturing method achieved by the present invention, it is possible to relatively simply manufacture a heat exchanger having the above-mentioned effect in the patent application scope item No. 2. The method for manufacturing a heat exchanger achieved by the present invention is that in the method for manufacturing a heat exchanger described in item 14 of the scope of patent application, it is prepared to be formed by bending a pipe without a welded joint The Z-shaped curved tube and the two through-holes are a plurality of plate-shaped radiators formed at intervals in the front-rear direction. By passing the Z-shaped curved tubes through the through-holes of all the plate-shaped radiators, a plurality of them are arranged in parallel The non-fixed heat sink group formed by the plate-shaped heat sink is provided in a predetermined number in a straight direction where the straight pipe portion is bent in the length direction of the straight pipe portion, and the predetermined number is set to be in a Z shape On the side of the curved part of the curved tube, and the first heat sink group is formed of two or more non-solid-15-f 200301343 n times the number of fixed heat sink groups (n is an integer of 2 or more), and the pipe is fixedly expanded. Z-shaped curved tubes so that each plate-shaped heat sink spans two straight tube portions to obtain a divided fin group forming a second fin group and a ζ-shaped curved shape with fins having the first fin group Tube 'and will form all the divided heat sink groups The plate-shaped heat sink is divided into a portion where one straight tube portion is fixed and a portion where the other straight tube portion is fixed to form a second heat sink group, which includes two Z-shaped curved tubes with heat sinks. A meandering tube with fins formed by bending the straight tube portion outward in the front-rear direction. The heat exchanger manufacturing method 'achieved by the present invention is a simpler way to manufacture a heat exchanger having the above-mentioned effects in the patent application range of item 14. In the manufacturing method of the two types of heat exchangers of the present invention, the 'internal fins extending on the inner peripheral surface of the Z-shaped curved tube and extending along the longitudinal direction thereof' are formed integrally at intervals in the circumferential direction. In the two manufacturing methods of the heat exchanger of the present invention, the expansion of the Z-shaped curved tube is performed using a fluid. In the manufacturing method of the two kinds of heat exchangers of the present invention, two types of self-spoon internal fins are formed from the inner peripheral surface of the Z-shaped curved tube with different protruding heights, and are arranged interactively in the circumferential direction. , The protruding height of the higher internal heat sink is 0. 7 ~ 1 · 7mm, the protruding height of the lower inner fin is 0 · 4 ~ 1 · 2mm 〇The heat of the present invention is provided with two types of inner fins on the inner peripheral surface of the Z-shaped curved tube. In the manufacturing method of the exchanger, the pitch of the internal fins is formed as 0. 4 ~ 1. 6 m m. On the inner peripheral surface of the Z-shaped curved tube, there are two types of internal heat dissipation -16-sheets. In the manufacturing method of the heat exchanger of the present invention, the outer diameter of the z-shaped curved tube is 6 to 10 mm. The thickness of its peripheral wall is formed to 0. 4 ~ 0. 8 mm. In the manufacturing method of the two kinds of heat exchangers of the present invention, the heights of all the internal radiators are equal, and the protruding height of the internal fins from the inner peripheral surface of the Z-shaped curved tube is formed as 0. 7 ~ 1 · 2mm. In the manufacturing method of the two heat exchangers of the present invention in which the heights of all the internal heat sinks are equal, the pitch of the internal heat sinks is formed as 〇. 4 ~ 1. 6mm 0 In the manufacturing method of the two heat exchangers of the present invention in which the heights of all the internal fins are equal, the outer diameter of the Z-shaped curved tube is 6 to 10 mm. The thickness of the peripheral wall is formed as 0.4. ~ 〇. 8mm. In the manufacturing method of the two types of heat exchangers of the present invention, the plate-shaped heat sink forming the second fin group and constituting the divided fin group is formed by combining two types of fin forming portions and two fin forming portions. The connection portion is integrally formed in a separable shape. In this case, the Z-shaped curved tube can be easily installed while passing through the through hole of the plate-shaped radiator, and at the same time, it can be simply divided into plate-shaped radiators in subsequent processes. In the method for manufacturing two types of heat exchangers of the present invention, a plate-shaped heat sink constituting a first fin group and a plate-shaped heat sink composed of a divided fin group forming the second fin group are formed. It has the same shape. In the plate-shaped heat sink constituting the divided fin group, at least one of the upper and lower sides of the upper and lower sides has a V-shaped notch formed on the central portion in the front-rear direction. At the point where the marks meet, a crack extending in the up-down direction is formed without interfering with the score. In this case, when stamping a plate-shaped heat sink with a crack-17-, a stamping mold for stamping the other plate-shaped heat sink may be used. And the crack formation part is detachable, and two types of plate heat sinks can be formed using one type of stamping die. As a result, the manufacturing cost of the plate-shaped heat sink can be reduced. In addition, a V-shaped notch is formed in a central portion of at least one of the upper and lower sides of the plate-shaped heat sink constituting the divided heat sink group in the front-rear direction, and is aligned with the score in the front-rear direction. In this position, a crack extending in the up-and-down direction is formed so as not to interfere with the notch, so the division of the plate-shaped heat sink can be easily performed. In the manufacturing method of the two kinds of heat exchangers of the present invention, after dividing the divided fin group to form a second fin group, the second fin group having a predetermined number in the Z-shaped curved tube with fins can be cut. Group of straight tubes. [Embodiment] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. In this embodiment, the heat exchanger of the present invention is applied to an evaporator of a cooling device. In the following description, the term "aluminum" refers to a substance containing an aluminum alloy other than pure aluminum. Figures 1 and 2 show the coiled tube with fins used to form the evaporator. Figure 3 shows the evaporator. In addition, FIG. 4 shows a Z-shaped curved tube with fins for forming a meandering tube with fins, and FIG. 5 shows a plate-shaped heat sink. In Fig. 1 and Fig. 2, the meandering tube (1) with fins is provided with: an aluminum meandering tube (2), which is provided at three or more positions in the front-rear direction (here, four positions) Straight tube section (2 a); the majority (here two) the first heat sink group -18- 2υύ301- ^ 3 (2), which are two adjacent to the central section of the snake tube (2) The straight tube portion (2a) is arranged at intervals in the length direction; most (here, 2) second fin groups (4) are connected to the straight tube portions at the front and rear ends of the meandering tube (2) ( 2 a), which are arranged at intervals in the longitudinal direction. The interval between the two first fin groups (3) and the two second fin groups (4) is such that the straight pipe portions (2a) are formed so that each of the first fin groups (3) and each of the second fin groups The radiating fin group (4) is folded back to a curved length. The meandering tube (2) is formed by bending a tube without a welded joint, and on its inner peripheral surface, it extends in its length direction and protrudes into two different types of internal heat sinks (heights differing). 20) (2 1), which are formed in an interactive shape with spaces in the circumferential direction and spaced in the circumferential direction to form an integrated shape. The internal heat sink (20) (21) is protruded toward the center of the meandering tube (2). And the protruding height (hi) of the inner peripheral surface of the meandering tube (2) by the higher internal heat sink (20) is 0. 7 ~ 1. 7mni, the protruding height of the lower internal heat sink (21) is 0. 4 ~ 1. 2 mm. In addition, the pitch (P) of the internal heat sink (20) (21) is formed as 0. 4 ~ 1. 6mm. Here, the pitch (P) of the internal heat sink (20) (2 1) is, in a cross section, the center line connecting the meandering tube (2) and two adjacent internal heat sinks (20 ) (2 1) The distance in the circumferential direction on the outer peripheral surface of the meandering tube (2) between 2 straight lines (L1) (L2) in the thickness center. In addition, the outer diameter of the 'snake tube (2) is formed to 6 to 10 mm, and the thickness of its peripheral wall is formed to 0. 4 ~ 〇. 8mm. The heat sink group (3) of the table 1 is formed by a plurality of side-by-side aluminum plate-shaped radiators (5) that span two straight tube portions (2a) and are fixed to the two straight tube portions (2a). The plate-shaped heat sink (5) is a long rectangle in the front-rear direction. Hereinafter, the plate-shaped heat sink (5) constituting the first fin group (3) is referred to as a first plate-shaped heat sink. The second heat sink group (4) is formed by a plurality of aluminum plate-shaped heat sinks (6) fixed to each straight pipe portion (2a), and is formed in a longitudinal direction with respect to the straight pipe portion (2a). The first fin group (3) has the same position. The length of the plate-shaped heat sink (6) of the second heat sink group (4) in the front-back direction is equal to 1/2 of the length of the first plate-shaped heat sink, or formed only shorter than the cuts (1 2) and cracks described later. (1 3). Hereinafter, the plate-shaped heat sink (6) constituting the second fin group (4) is referred to as a second plate-shaped heat sink. The heat sink pitch of the first heat sink group (3) and the second heat sink group (4) may be different, and the heat sink pitch of the second heat sink group (4) is larger than the first heat sink. The heat sink pitch of the chip group (3) is preferred. With regard to the first heat sink (5), two through holes (5a) are formed at intervals in the front-rear direction, and the two straight tube portions (2a) of the center portion of the meandering tube (2) pass through all of them. The through hole (5a) of the first plate-shaped radiator (5) is fixed around the two straight-tube portions (2a) by expanding the two straight-tube portions (2a). . A through hole is formed in the second plate-shaped heat sink (6), and the straight pipe portions (2a) of the meandering tube (2) are passed through the through holes of the second plate-shaped heat sink (6), respectively. The second plate-shaped radiator (6) is fixed around the straight pipe portion (2a) by expanding the two straight pipe portions (2a). In addition, the coiled tube (1) with fins can be maintained as an evaporator. Next, as shown in FIG. 3, the meandering tube (1) with fins is between the first fin group (3) adjacent to the first fin group (3) adjacent to the entire straight tube portion (2a) of the meandering tube (2). Among the two fin groups (4), each of the first fin groups (3) and each of the second fin groups (4) are formed in a curved shape such that they overlap each other, thereby forming an evaporator (E). That is, in this type of evaporator (E), the two first fin groups (3)-2 0-are arranged in a layered manner in the up-down direction, and the first fin group (3) On the front and back sides, two second heat sink groups (4) are stacked in the up-and-down direction, and two front and rear heat sinks (5) of each first heat sink group (3) are placed on the front and back. The straight tube portion (2b) is penetrated, and one straight tube portion (2b) is penetrated on the second plate-shaped heat sink (6) of each second fin group (4). In addition, on the left side than the heat sink group (3) (4), the upper and lower straight pipe portions (2b) are connected by an integrally formed curved portion (2c) in the same position in relation to the front-rear direction. . In addition, in the right side of the heat sink group (3) (4), the two systems at the front and rear sides in the upper straight tube portion (2b) are respectively formed into one body and connected by the curved portion (2d). In the lower straight pipe part (2b), the two central parts are integrally formed with it and connected by a curved part (2e). Next, the manufacturing method of an evaporator is demonstrated. First, a Z-shaped curved tube (Η) with fins shown in FIG. 4 is manufactured. That is, there are prepared (refer to FIG. 5): a Z-shaped curved tube (1 0) formed by bending an aluminum tube without a welded joint; most aluminum first plate radiators ( 5), spaced in the front-back direction and forming two through holes (5a); most aluminum plate radiators (1 1), spaced in the front-back direction and forming 2 through-holes ( 1 1 a). On the inner peripheral surface of the Z-shaped curved tube (1 0), there are two types of internal heat sinks (20) (2 1) extending in the length direction and protruding at different heights, which are separated in the circumferential direction. Interspaced and integrally formed. The internal heat sink (2 0) (2 1) is the same as shown previously with reference to FIG. 2. As shown in (a) and (b) of Figure 5, the plate heat sinks (5) (1 1) are long rectangles in the front-rear direction, and one of the plate heat sinks (11) -21- V-shaped notches (1 2) are formed on the central portion in the front-back direction of the upper and lower edge portions, and a plate-shaped heat sink (1 1) is formed between the two notches (1 2). The crack (1 3) extending in the width direction (up and down direction). The through hole (1 1 a) is formed before and after the crack (1 3). The interval between the two nicks (1 2) and the two cracks (1 3) is preferably set to be about 0 · 1 to 0 · 4 mm. Hereinafter, the plate-shaped heat sink (1 1) having nicks (1 2) and cracks (1 3) is referred to as a plate-shaped heat sink with cracks. The plate-shaped heat sink (1 1) with cracks is such that the cutting mark forming part and the crack forming part can be disassembled freely on a stamping die used for press-forming the first plate-shaped heat sink (5). Formed by stamping. Here, by forming nicks (1 2) and cracks (1 3), the plate-shaped heat sink (1 1) with cracks is formed by two heat sink forming portions (1 5) located in front and back, and nicks (1 2) is formed between the crack (1 3) and the connection portion (1 6) integrally connected to the two fin formation portions (1 5) which can be divided. In addition, the two straight pipe portions (10a) of the Z-shaped curved pipe (10) are passed through the two through holes (5a) (11a) of all the plate-shaped heat sinks (5) (11). The non-fixed heat sink group formed by a plurality of plate-shaped heat sinks (5) (1 1) is spaced apart from each other in the length direction of the straight pipe portion (2a), and a plurality of them are provided (here, four). At this time, the two non-fixed heat sink groups on the curved portion (1 Ob) side of the Z-shaped curved tube (1 0) are formed by the first plate-shaped heat sink (5), and are formed with heat dissipation. The first heat sink group (3) of the meandering tube (1). In addition, the two non-fixed fins on the open side of both ends of the Z-shaped curved tube (1 0) are formed by a plate-shaped heat sink (1 1) with cracks, and meandering with fins The second heat sink group (4) of the tube (1). The interval between the non-fixed heat sink groups forming the first heat sink group (3) is such that the lengths of the two straight pipe portions (10a) are bent as if the first heat sink groups (3) -22- are overlapped, and It becomes equal to the interval between the non-fixed heat sink groups forming the second heat sink group (4). In addition, the total number of non-fixed heat sink groups is η times the number of non-fixed heat sink groups forming the first heat sink group (4) (11 is an integer of 2 or more). Then, in this state, pressure fluids such as water, oil, and air are introduced into the Z-shaped curved tube (10) to expand the tube, and the first plate-shaped radiators of the non-fixed heat sink groups ( 5) Fixing the plate-shaped heat sink (11) with cracks around the two straight pipe portions UOa) of the Z-shaped curved pipe (10) to produce two divided heat sinks (4) Radiating fin group (1 4), and two first fin group (3) with fins Z-shaped curved tube (Η) (see FIG. 4). In addition, the expansion of the Z-shaped curved tube (10) can also be performed as follows, that is, a tube-expanding tool having a mandrel for expanding the tube is prepared before pressing the rod, and the Z-shaped curved tube (1 〇) Press the mandrel for pipe expansion of the pipe expansion tool into the straight pipe section (2a). Then, a Z-shaped curved tube (Η) with fins was used to manufacture a meandering tube (1) with fins. That is, first, a plate-shaped heat sink (1 1) with a crack, which constitutes two divided fin groups (1 4) of the Z-shaped curved tube (10), is formed into a score (1 2). In the connecting portion (1 6) between the crack (1 3), a portion fixed to one straight pipe portion (10a) and a portion fixed to the other straight pipe portion (10a) are divided into A second heat sink group (4) is formed. The cracked plate-shaped heat sink (1 1) is divided by pressing the wedge into the two notches (1 2) and pulling the wedge in the front-back direction. Next, the two straight tube portions (丨 〇a) of the Z-shaped curved tube (1 0) with the fin-shaped Z-shaped curved tube (Η) are attached to the bent portion side of the ζ-shaped curved tube (1 0). The two first heat sink groups (3) and the 3-23rd second heat sink groups (4) are respectively bent outward in the front-rear direction (refer to the chain line in FIG. 1). In this way, in the meandering tube (2), the manufactured meandering tube (1) with fins is provided with: most of the first fin group (3) 'are connected to two straight tube portions adjacent to the central portion ( 2 a) are arranged at intervals in the length direction; and most of the second fin group (4) are spaced at intervals in the length direction of the straight tube portion (2 a) before and after the meandering tube (2). And the setter. Finally, the meandering tube (1) with fins is in a portion between the first fin group (3) and the second fin group (4) adjacent to each other in the straight pipe portion (2a). Each of the first fin group (3) and each of the second fin group (4) are formed in a curved shape such as overlapping with each other, thereby forming an evaporator (E) (refer to the chain line in FIG. 3). The refrigeration cycle included in the evaporator (E) is an evaporator having a compressor, a condenser, and an evaporator, and a cooling device such as a refrigerator using a hydrocarbon-based cold coal as a cold coal, or a refrigerated display case. In such a cooling device, the amount of cold coal circulation is formed to a low circulation amount of 1 to 9 kg / h. In the above embodiment, the number of the straight tube portions (2 a) of the meandering tube (2) in the meandering tube (1) with a radiator used to form the evaporator (E) is four. In the Z-shaped curved tube (Η), the number of divided fin groups (1 4) formed by the plate-shaped heat sink (1 1) with cracks is equal to the number of the first fin group (3) However, it is not limited to this, and the number of the straight pipe portions (2 a) may be any number of 2 η (η is an integer of 2 or more). In this case, in the Z-shaped curved tube (Η) with a radiator, the number of divided fin groups (1 4) formed by the plate-shaped radiator (1 1) with a crack is set to be the first (Η-1) times the number of heat sink groups (3). In addition, in the Z-shaped curved tube (Η) with a radiator, -24-the two straight tube portions (1 0 a) of the Z-shaped curved tube (1 ο) are serpentine outward in the forward-backward direction. Bend to form a meandering tube with fins. In addition, the number of the straight tube portions (2 a) of the meandering tube (2) in the meandering tube (1) with fins is a case where an odd number of 3 or more is formed, that is, 2n-1 (η is 2 The above integer), but in this case, after dividing the plate-shaped radiator (1 丨) with a crack in the divided fin group (1 4), the Z-shaped curved tube (10) One of the square straight pipe portions (10a) is truncated to have a length from its open end to the second heat sink group (4) having the same number as the first heat sink group (3). In addition, in the above-mentioned embodiment, the first fin group (3) and the second fin group (4) of the evaporator are respectively provided in the upper and lower stages, but it is not limited to this, and may also be provided in the upper and lower stages. the above. In this case, the number of the first fin group (3) and the second fin group (4) in the meandering tube (1) with a radiator is set to 3 or more. In addition, the number of the first heat sink group (3) and the second heat sink group (4) may be one. Furthermore, in the above-mentioned embodiment and other embodiments, it is not necessary to form cracks (1 3) and nicks (12) in the plate-shaped heat sink to be divided. In addition, the heat exchanger of the present invention is an object other than an evaporator of a cooling device. Figure 6 shows a modified example of the meandering tube (2) with a finned meandering tube (1) for forming an evaporator. In Fig. 6, most inner fins (22) extending along the lengthwise direction of the meandering tube (2) and having the same protruding height are formed integrally with intervals in the circumferential direction. From the internal heat sink (2 2), the meandering tube (h3) of the inner 13 sides of the meandering tube (2) -25- is 0. 7 ~ 1. 2mm. In addition, the pitch (p) of the internal heat sink (22) is 0. 4 ~ i 6mm. Here, the pitch (P) of the internal heat sink (22) is the same as described above. In addition, the outer diameter of the meandering tube (2) is 6 ~ 10mm ’, and the wall thickness of the peripheral wall is Q. 4 ~ 0. 8mni. [Effects of the invention] [Possibility of industrial use] The heat exchanger of the present invention is used as an evaporator of a cooling device such as a refrigerator or a refrigerated display case, and is particularly suitable for the use of hydrocarbons _ cold coal The evaporator of the cooling device. [Brief description of the drawings] Figure 1 is a perspective view of a coiled tube with a heat sink for forming an evaporator suitable for the present invention. Figure 2 is an enlarged sectional view taken along the line I I-I I in Figure 1. Figure 3 is a perspective view of an evaporator suitable for the present invention. Figure 4 is a perspective view of a Z-curved tube with fins for forming a meandering tube with fins. · Figure 5 (a) and (b) are front views of two types of plate radiators. Another specific example of the meandering tube with a fin shown in Fig. 6 is a cross-sectional view corresponding to Fig. 2. Figure 7 is a perspective view of a conventional evaporator. [Description of Representative Symbols of Main Parts] 1, 2: Snake tube, Snake tube with heat sink 1 〇, H: Z-shaped curved tube 1 2: Scoring-2 6-0301543 1 3: Crack 2 0, 2 1: Internal fins 2 a, 10 a: Straight tube section 3: First fin group 3 0: Evaporator 32: Radiator group 33: Straight tube 3 4: U-shaped elbow tube 4: Second fin group 5 a : Through holes 6, 5, 1 1, 31: Plate heat sink E: Evaporator hi, h2: Protruding heights L1, L2: Straight
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