(1) 1273172 九、發明說明 【發明所屬之技術領域】 本發明，是有關容積形流體機械的一種也就是渦卷形 流體機械，特別是有關作動流體是使用了 R404 A、R5 07 A 、R5 0 8B、R4 10A、碳化氫、二氧化碳、氨等的冷媒的使 用於冷凍冷藏用的渦卷式壓縮機。 φ 【先前技術】 在冷凍用機器的冷凍循環系統中較佳的壓力比是4〜 20，冷凍循環系統是使用渦卷式壓縮機的情況時，除了增 大由渦卷式壓縮機的渦卷體（渦卷渦圈）形成的壓縮室的吸 入完成時的容積及吐出開始時的容積的比（以下稱設計容 積比）以外，無其他可達成如此壓力比的手段。且，在壓 縮機無法大型化的有限的外徑內，欲增加設計容積比是困 難的。 φ 日本特開平7-27065號公報（以下稱專利文獻1)中，構 成繞轉渦卷渦卷體及固定渦卷渦卷體的基本渦曲線是使用 代數螺線。由此容積變化率的設定成爲可能，由圓的漸開 線設計的情況相比因爲容積變化率可較大，所以可提高性 能’避免因冷媒的壓縮不足所產生的動力的降低。 [專利文獻1]日本特開平7-2 7065號公報 【發明內容】 (本發明所欲解決的課題） -5- (2) 1273172 專利文獻1是對於容積變化率的設定很有用，渦卷體 的捲取開始部的厚度（渦圈厚度）雖可以形成比其他的部分 厚的形狀，但是例如與習知機同等的裝置尺寸中雖可確保 信賴性，卻未充分檢討有關增加設計容積比的部分。即， 專利文獻1是揭示：例如動徑r、偏角0、代數螺線的係數 爲a、代數螺線的指數爲k時，在r = a 0 k(式1)的代數螺線曲 線中變化代數螺線的係數a或是代數螺線的指數k，來加大 φ 供提高作動流體的壓力用的渦卷體的捲取開始部的渦圈厚 度。在此對於作動流體的信賴性，是加大渦卷體的捲取開 始部的渦圏厚度，爲了不改變裝置尺寸地提高壓力比而增 加渦卷體的捲取角，即渦卷體不會變廣地形成渦圈。如此 的話，繞轉渦卷的渦卷體及非繞轉渦卷的渦卷體的渦圈厚 度，會在偏角0變大的渦卷體結束部變薄。特別是，對於 在繞轉渦卷的渦卷體最外周部分及非繞轉渦卷的內周壁的 吸入完成時形成壓縮室的一種組合了非對稱渦圈的渦卷式 # 壓縮機，因爲在渦圈厚度薄的繞轉渦卷的渦卷體捲取結束 部返覆地與非繞轉渦卷的渦卷體（渦圈）線接觸，所以信賴 性就成爲問題。在此只由變化式1的代數螺線的係數a或是 代數螺線的指數k，無法同時兼顧增大渦卷體捲終部渦圈 厚度、及增大設計容積比，並確保信賴性。 本發明的目的提供一種渦卷式壓縮機，對於具有渦卷 體的渦卷式壓縮機，可增大設計容積比且即使在高壓力比 的運轉下，仍具有高信賴性。 -6- (3) 1273172 (用以解決課題的手段） 爲了達成上述目的用的本發明的渦卷式壓縮機，是具 有壓縮機構，該壓縮機構爲：將由極座標形式表示的代數 螺線曲線作爲基本渦曲線而具備依據此基本渦曲線的包絡 線所形成的側面形狀的渦卷體是具備對於端板直立設置的 繞轉渦卷及非繞轉渦卷，將此繞轉渦卷及非繞轉渦卷的前 述渦卷體朝向內側的狀態下相互嵌合，使前述繞轉渦卷對 Φ 於前述非繞轉渦卷的表面上不自轉的方式以預定的半徑進 行公轉運動，藉由縮小前述2個渦卷的渦卷體間所產生的 密閉空間內的流體的體積來進行壓縮作用；其特徵爲：前 述2個渦卷之中至少前述繞轉渦卷的渦卷體，是具有該渦 卷體的基本渦曲線及包絡線的距離不同的部分。 如上述，具有將代數螺線曲線作爲供形成渦卷體用的 基本渦曲線並由基本渦曲線的包絡線構成該形狀的繞轉渦 卷的渦卷體（繞轉渦卷體）及非繞轉渦卷的渦卷體（非繞轉 • 渦卷體），其中至少繞轉渦卷的渦卷體，是具有渦卷體的 基本渦曲線及包絡線的距離爲不同的部分。依據此結構的 話，可任意變化繞轉渦卷的渦卷體的渦圈厚度而增大設計 容積比，就可提供在高壓力比運轉下信賴性高的渦卷式壓 縮機。特別是，藉由將非繞轉渦卷的渦卷體及繞轉渦卷的 渦卷體相互嚙合組合，就可形成一對密閉空間，其於繞轉 渦卷的渦卷體的內側及外側吸入完成時的內容積也就是壓 退容積爲相互不同，即所謂具有非對稱渦圈的渦卷式壓縮 機，爲了加厚其繞轉渦卷的吐出側也就是捲取開始部的渦 (4) 1273172 圈厚度，並提高設計容積比，而形成渦卷體的捲取角多的 繞轉渦卷的渦卷體的情況時，因爲可不需要增多渦卷體的 捲取角而可擴大繞轉渦卷的捲取結束部的寬，所以可以確 保信賴性並同時提高設計容積比。 且，對於上述的本發明的渦卷式壓縮機，前述繞轉渦 卷的渦卷體的基本渦曲線及包絡線的距離不同的部分，是 包含該渦卷體的渦曲終端部也可以。此情況，即使捲取開 φ 始部分的渦圈厚是比其他的渦圈厚更厚的方式設置繞轉渦 卷的渦卷體，以代數螺線曲線爲基準渦曲線的渦卷體的捲 取結束部的渦圈厚不需變薄，就可以獲得從捲取開始至捲 取結束爲止具有所期厚度的渦卷體。 且，對於上述的本發明的渦卷式壓縮機，前述繞轉渦 卷的渦卷體的基本渦曲線及包絡線的距離不同的部分的距 離，是比其他的部分更遠也可以。此情況也同樣，即使捲 取開始部分的渦圈厚是比其他的渦圈厚更厚的方式設置繞 % 轉渦卷的渦卷體，以代數螺線曲線爲基準渦曲線的渦卷體 的捲取結束部的渦圈厚不需變薄，就可以獲得從捲取開始 至捲取結束爲止具有所期厚度的渦卷體。 且，對於上述的本發明的渦卷式壓縮機，前述基本渦 曲線也就是代數螺線曲線，是動徑爲r、偏角爲0、代數 螺線的係數爲a、代數螺線的指數爲k時，可由r = a 0 k(式1) 表示也可以。這時繞轉渦卷的渦卷體的基本渦曲線及包路 線的距離不同的部分，是在該渦卷體的任意的偏角0的區 間內形成不同也可以。在從該渦卷體的渦曲終端部起3 6 0 (5) 1273172 度以內的偏角0的區間內不同也可以。此情況，具有將代 數螺線曲線作爲供形成渦卷體用的基本渦曲線構成的繞轉 渦卷的渦卷體（繞轉渦卷體）及固定渦卷的渦卷體（固定渦 卷體），將構成前述繞轉渦卷體外側壁面（內側壁面）的基 本渦曲線及包絡線的距離減少（增加）任意的偏角0。且， 同時於固定渦卷體內側壁面（外側壁面）之中，與繞轉渦卷 體外側壁面（內側壁面）同一的偏角0中，使基本渦曲線及 φ 包絡線的距離只增加（減少）繞轉渦卷體所減少（增加）的部 分。由此對於任意的偏角0皆可變化繞轉渦卷體的渦圈厚 度，就可保障2個渦卷體可幾何學地接觸。特別是在從該 渦卷體的渦曲終端部起3 6 0度以內的偏角0的區間內形成 不同也可以。 且，從繞轉渦卷體外側壁面的任意的偏角0至捲完爲 止的區間中，以基本渦曲線及包絡線的距離作爲偏角0的 係數而使該區間內的距離漸漸地減少也可以，同時固定渦 φ 卷體內側壁面之中，在與繞轉渦卷體外側壁面同一區間內 ，只增加在繞轉渦卷體所減少的部分的方式使基本渦曲線 及包絡線的距離也同樣作爲偏角0的係數。由此，不需大 改變繞轉渦卷體的外徑就可增加繞轉渦卷體的渦圈厚度。 進一步爲了達成上述目的，本發明的渦卷式壓縮機， 是具有壓縮機構，其具備渦卷體是對於端板直立設置的繞 轉渦卷及非繞轉渦卷，將此繞轉渦卷及非繞轉渦卷的前述 渦卷體朝向內側的狀態下相互嵌合，使前述繞轉渦卷對於 前述非繞轉渦卷在表面上不自轉的方式以預定的半徑進行 -9- (6) 1273172 公轉運動，藉由縮小前述2個渦卷的渦卷體間所產生的密 閉空間內的流體的體積來進行壓縮作用，其特徵爲：前述 繞轉渦卷的渦卷體的外側側面及成爲密閉空間的前述固定 渦卷內側側面、及該固定渦卷的渦卷體的內側側面及挾持 設置前述繞轉渦卷的渦卷體的前述固定渦卷的渦卷體的外 側側面之間的前述固定渦卷的渦卷體間距離，是使最外周 的渦卷體間距離比其他的渦卷體間距離大。 p 藉由具備這種結構，繞轉渦卷的渦卷體及固定渦卷的 渦卷體的最外周部分相互接觸的區間內，藉由使固定渦卷 的渦卷體的渦圈間距離比其他的區間的渦圈間距離更大， 就可使繞轉渦卷的渦卷體捲取結束部的渦圈寬加大至與其 他的部分同等以上，而可以提高繞轉渦卷的信賴性，並可 以提高渦卷式壓縮機的性能。 進一步，將本發明所適用的渦卷式壓縮機使用於冷凍 循環系統的冷凍用機器，因爲只由與習知的大小不變的壓 φ 縮機的外形尺寸，就可獲得所期的壓力比，所以冷凍用機 器中的冷凍循環系統所佔有的領域，可形成比非冷凍物的 領域更大。 (發明之效果） 依據本發明，可以提供一種渦卷式壓縮機，可增大設 計容積比，且高壓力比運轉下的信賴性高。 【實施方式】 -10- (7) 1273172 以下，藉由第1圖乃至第6圖說明本發明的實施例。 第1圖是本發明的一實施例的渦卷式壓縮機的縱剖面 圖。渦卷式壓縮機11，是具備：繞轉渦卷1及非繞轉渦卷 之一的固定渦卷3、旋轉繞轉渦卷1的曲柄軸1 2、支撐曲柄 軸1 2的框架（車架）1 3、容許繞轉渦卷1的公轉運動並防止 自轉運動的歐丹環1 4、驅動曲柄軸用的馬達1 5等。 在此，兩渦卷1、3的渦卷體是依據代數螺線曲線的包 φ 絡線形成。本實施例所使用的代數螺線曲線，是動徑r、 偏角0、代數螺線的係數爲a、代數螺線的指數爲k時’可 由r = a 0 k(式1)表示。藉由以此曲線爲基本渦曲線的包絡線 來決定各渦卷的渦卷體1、3的形狀，就可作動流體的壓力 高的渦卷體的捲取開始部的渦圈厚度比其他的部分更大， 與漸開線曲線相比，在相同面積下可以增加捲數。藉由適 宜設定式1的代數螺線的係數a、代數螺線的指數k，與漸 開線曲線相比可以在相同面積下增加捲數的話，各渦卷體 φ 1、3的渦圈厚度會朝向捲取結束部漸漸地減少。在此，藉 由使包絡線及基本渦曲線的距離配合偏角變化，就可形成 具備任意的偏角的渦圈厚度的形狀，特別是，在捲取結束 部需要渦圈厚度的範圍內變化包絡線及基本渦曲線的距離 就可獲得所期的形狀。對於渦卷體1、3的形狀如後述。 如此結構的渦卷式壓縮機，藉由將馬達1 5通電來使曲 柄軸1 2旋轉，繞轉渦卷1非藉由歐丹環1 4進行自轉運動而 是進行公轉運動。藉由兩渦卷1、3所形成的密閉空間的容 積來縮小從吸入配管1 6流入的低溫低壓的被壓縮流體並進 -11 - (8) 1273172 行壓縮作用。由密閉空間內所壓縮的被壓縮流體因爲成爲 高溫高壓，所以從冷凍循環取出的低溫的液體的被壓縮流 體會通過噴射配管17流入壓縮室內，壓縮過程的途中吐出 時，成爲氣體的被壓縮流體的溫度會下降。經過壓縮過程 而成爲高溫高壓的被壓縮流體，會從吐出口 7被排出至壓 縮機殼內，通過殼及殼內的壓縮機構成零件之間，從吐出 配管18被排出至冷凍循環內。 § 第2圖是顯示本發明的一實施例的渦卷式壓縮機的渦 卷形狀的平面圖。在第2圖中，繞轉渦卷的渦卷體（繞轉渦 卷體）2是具備繞轉渦卷體外側壁面2〇及繞轉渦卷體內側壁 面2i ’非繞轉渦卷的渦卷體（在本實施例中稱固定渦卷體）4 是具備固定渦卷體外側壁面4〇及固定渦卷體內側壁面4i。 固定渦卷體4是直立於固定渦卷端板5。具體的構造， 如透過潤滑油膜與繞轉渦卷丨的渦圈先端面接觸的固定渦 卷體4被立設的固定渦卷端板5的齒底面5a的高度，是與固 #定渦卷端板的面高度不同。本實施例的情況，固定渦卷端 丰反5的內周壁是從固定渦卷體4連續而成爲固定渦卷體4的 內側壁面4i的一部分。如後詳述，繞轉渦卷體外側壁面2〇 上的a至b的部分及固定渦卷體內側壁面4i上的^至b，的部 分’是與本實施例中的基本渦曲線之間的距離ε Η會變化 的區間’即已增大了繞轉渦卷體2的渦圈厚度的部分。點a 及點a’以及點b及點b，的偏角是相同。點c ’是從固定渦卷體 @側壁面4i上的渦卷結束偏角只減少槪略36〇度偏角的位 匕’點c是位在與前述點c，相同偏角的繞轉渦卷體外側壁 -12- (9) 1273172 面2 〇上的位置。吸入口 6是供被壓縮前的流體流入用的開 口部。吐出口 7是供已被壓縮的流體流出用的部位。 在第2圖中，將繞轉渦卷體2及固定渦卷體4的渦卷開 始的開始角度旋轉1 8 0度且將固定渦卷體4的中心0及繞轉 渦卷體2的中心〇 ’只錯開繞轉半徑ε的方式相互嚙合。且 ，非繞轉渦卷3的渦卷體4、及繞轉渦卷1的渦卷體2相互嚙 合組合時，在繞轉渦卷1的渦卷體2的內側及外側，會形成 φ 吸入完成時的內容積也就是壓退容積相互不同的一對密閉 空間，繞轉渦卷體2及固定渦卷體4是形成非對稱渦圈。而 且第2圖的繞轉渦卷體2及固定渦卷體4的狀態，是顯示在 渦卷結束點e及捲角比此點e小（偏角Θ小）的點d時，繞轉 渦卷體2及固定渦卷體4相互接觸而藉由形成的繞轉渦卷體 外側壁面2〇及固定渦卷體內側壁面4i間的密閉空間，爲流 體吸入完成的狀態。 使用第3圖說明第2圖的繞轉渦卷體外側壁面2〇及固定 Φ 渦卷體內側壁面4 i的形狀。虛線8是供規定繞轉渦卷體外 側壁面2〇及固定渦卷體內側曲線4i的形狀用的基本渦曲線 ，由式所顯示的話，動徑r、偏角0、代數螺線的係數a、 代數螺線的指數k時，成爲式r = a 0 k(式1)。虛線9是供規定 繞轉渦卷體內側壁面2 i及固定渦卷體外側曲線4 〇的形狀用 的基本渦曲線。這2個虛線所顯示的基本渦曲線，是將渦 卷開始的開始角度旋轉1 8 0度，且捲取開始點是同一點〇 ，在第3圖中由連續虛線表示。繞轉渦卷體外側壁面2 〇上 的點f及固定渦卷體內側壁面4 i上的點Γ，是各別對應於第 -13- (10) 1273172 2圖的點d的壁面上的點。 虛線8上的點g是點f及Γ成爲同一偏角的基本渦曲線上 的點。繞轉渦卷體外側壁面2 〇上的點b及固定渦卷體內側 壁面4 i上的點b ’，各別是對應於第2圖的點e的壁面上的點 。虛線8上的點i是點b及b’成爲同一偏角的基本渦曲線上 的點。同樣地點h是點a及點a’成爲同一偏角的基本渦曲線 上的點。 § 第3圖（a)是顯示專利文獻所揭示的習知技術的渦圈形 成法，第3圖（b)是顯示本實施例的渦圏形成法。第3圖（a) 中將虛線8作爲基本渦曲線的繞轉渦卷體外側壁面2〇是由 式r = a 0 k+ ε Η(式2)所示的包絡線之中只有ε Η的內側曲線 ，固定渦卷體內側壁面4i是只藉由ε Η形成外側曲線，各 包絡線2〇、4i間的距離是分別成爲繞轉半徑ε (即ε =2丨 ε Η | )。 同樣地將虛線9作爲基本渦曲線的繞轉渦卷體內側壁 # 面2i，是由式r = a 0 k+ ε Η(式2)(但是虛線8是偏角偏離180 度。）所示的包絡線之中，只有e Η的外側曲線，固定渦卷 體外側壁面4〇是只有ε Η成爲內側的曲線。各包路線2i， 間的距離，分別成爲與將虛線8作爲基本渦曲線的繞轉 渦卷體外側壁面2〇及固定渦卷體內側壁面4i之間的距離同 樣的繞轉半徑ε。 對於此在第3圖（b)中，將繞轉渦卷體外側壁面2〇上的 點a至點b的區間的與虛線8的距離ε Η作爲偏角0的係數來 變化距離ε Η，使在第3圖（a)的ε Η漸漸變小，在渦卷結束 -14- (11) 1273172 點b成爲ε H f。且同時將在固定渦卷體內側壁面4 i上的點 a’至b’的區間的與虛線8的距離ε Η，作爲使只增加由繞轉 渦卷體外側壁面2 〇所減少的部分的偏角0的係數而在渦卷 結束點b’成爲ε ΗΓ，並將繞轉渦卷體外側壁面2〇及固定渦 卷體內側壁面4i的距離作爲繞轉半徑。（即，£=|£11〖，|-丨ε H f | )。藉此，繞轉渦卷體2的渦卷結束的渦圈厚度可 以只加厚偏角0的ε Η的差量。 • 在第4圖中，顯示從顯示繞轉渦卷體外側壁面2〇的包 絡線及顯示固定渦卷體內側壁面4 i的包絡線的基本渦曲線 的距離ε Η及偏角Θ的關係的一例。圖中線19是顯示本實 施例中的繞轉渦卷體外側壁面2〇及基本渦曲線也就是虛線 8的距離ε Η的變化，線20是顯示本實施例中的固定渦卷 體內側壁面4i及基本渦曲線也就是虛線8的距離ε Η的變化 。且虛線2 1是習知技術的距離ε Η。從渦卷開始角0 0至 偏角0 a爲止爲一定的値ε Η，偏角0 a至0 b是本實施例的 0 基本渦曲線及包絡線的距離變化的區間。 線19及線20，是成爲與線21的差分成爲同値的偏角（9 的係數式。第4圖（a)是基本渦曲線及包絡線的距離以偏角 0的1次係數變化的情況。第4圖（b)是偏角0 c的基本渦曲 線的距離是分別成爲ε Ht、ε Ht’地改變線19及線20的變 化率的情況。此外也可舉例由2次係數來變化變更區間的 方法等。 接著說明對於繞轉渦卷體2的渦卷結束渦圈厚度的增 大由上述的方法進行的情況、及習知技術也就是只有代數 -15- (12) 1273172 螺線的係數a及代數螺線的指數k變化的情況的設計容積比 的不同。第5圖（a)是利用本實施例，且第5圖（b)是利用習 知技術’增大繞轉渦卷體2的渦卷結束渦圈厚度的情況， 分別顯不各繞轉渦卷體2是由同一外徑r且同一渦卷結束渦 圈厚度T時的由繞轉渦卷體外側壁面2 〇及固定渦卷體內側 壁面4i形成的密閉空間l〇a爲流體吸入完成時的狀態的平 面圖。 • 且第5圖（c)及第5圖（d)是顯示第5圖（a)及（b)只進行任 意的角度公轉運動時的繞轉渦卷及固定渦卷的位置關係， 藉由繞轉渦卷體外側壁面2〇及固定渦卷體內側壁面4i所形 成的密閉空間1 〇b，兩圖中是顯示與同一徑也就是吐出口 7 導通之前的狀態。 設計容積比是密閉空間10a及密閉空間l〇b的比，2個 渦卷體的渦圈高度從渦卷開始至渦卷結束爲止爲一定的情 況時，表示將密閉空間10a及10b投影於繞轉渦卷端板或是 Φ 固定渦卷端板時的面積的比。圖中虛線8a至8d是由形成密 閉空間l〇a及10b的繞轉渦卷體外側壁面2〇及固定渦卷體內 側壁面4i的基本渦曲線沿著繞轉渦卷體外側壁面2〇描畫。 在此說明密閉空間的面積。從第3圖（a)可了解，密閉空間 l〇a的面積是與虛線8的點g至點i爲止的長度及繞轉半徑ε 的積幾乎同等。同樣地第5圖的密閉空間的面積是各別與 虛線8a至8 d的長度及繞轉半徑ε的積幾乎同等。藉此，設 計容積比的比較是藉由比較供形成前述各別的密閉空間用 的基本渦曲線的長度就可判明。 -16- (13) 1273172 第6圖是比較了第5圖的虛線8a至8d的長度的圖表。圖 中長度1是將虛線8a的長度指標化的長度，長度2是表示對 於虛線8a的虛線8b的長度的比。同樣地長度3是將虛線8c 的長度指標化的長度，長度4是表示對於虛線8c的虛線8d 的長度的比。依據本實施例可了解，進行渦圈厚度的增大 時的設計容積比是比習知技術的設計容積比更大。 藉由以上利用本實施例就可達成將繞轉渦卷以同一外 φ 徑增大渦卷結的束厚度時的設計容積比的擴大。而且，如 此由與習知的尺寸幾乎相同尺寸的渦卷零件所組成，且將 本發明所適用的壓力比已增大的渦卷式壓縮機搭載於冷凍 循環系統的冷凍冷藏用機器，是幾乎不改變習知的冷凍循 環的尺寸就可獲得高壓力比，可以確保信賴性高且效率佳 的運轉。 如到此爲止所述，依據本發明的實施例將代數螺線曲 線作爲渦卷體的基本渦曲線，藉由將形成與繞轉渦卷體外 # 側壁面及固定渦卷體內側壁面的基本渦曲線的包絡線及基 本渦曲線的距離作爲代數螺線的偏角的係數加以變化，即 使繞轉渦卷體的外徑同一且繞轉渦卷體渦卷結束部渦圈厚 與其他的部分的厚度略同一也可達成設計容積比的擴大。 由此可確保渦圈渦卷結束的信賴性且防止高壓力比運轉時 的壓縮不足所導致的圖示動力的增加並可以提高效率。 【圖式簡單說明】 [第1圖]本發明的一實施例的渦卷式壓縮機的縱剖面 -17- (14) 1273172 圖。 [第2圖]本發明的一實施例的渦卷式壓縮機的渦卷體 的平面圖。 [第3圖]本發明的一實施例的渦卷式壓縮機的渦卷體 的構成法。 [第4圖]本發明的一實施例的構成基本渦曲線及渦卷 體壁面的包絡線的距離的圖表。 p [第5圖]本發明的一實施例及由習知技術形成的繞轉 渦卷體及固定渦卷體中，比較了由繞轉渦卷體外側壁面及 固定渦卷體內側壁面所形成的密閉空間爲流體吸入完成時 及吐出之前的狀態的平面圖。 [第6圖]比較了第5圖中的基本渦曲線的長度的圖表。 【主要元件符號說明】 1 :繞轉渦卷 籲2 :繞轉渦卷體 2i :繞轉渦卷體內側壁面 2〇 :繞轉渦卷體外側壁面 3 :固定渦卷（非繞轉渦卷） 4 :固定渦卷體 4 i ·_固定渦卷體內側壁面（曲線） 40 :固定渦卷體外側曲線 5 ·固定渦卷端板 5a :齒底面 -18- (15) 1273172 6 :吸入口 7 :吐出口 8 :基本渦曲線 8 a :虛線 8 b .虛線 8c.虛線 8 c :虛線 8 d ·虛線 9 :虛線 1 0 :密閉空間 1 0 a :密閉空間 l〇b :密閉空間 1 1 :渦卷式壓縮機 1 2 :曲柄軸 13 :框架（車架） φ 1 4 :歐丹環 1 5 :馬達 1 6 :吸入配管 1 7 :噴射配管 1 8 :吐出配管 19 :線 20 :線 21 ·虛線 -19(1) 1273172 IX. Description of the Invention [Technical Field of the Invention] The present invention relates to a scroll-shaped fluid machine for a volumetric fluid machine, and particularly relates to an actuating fluid using R404 A, R5 07 A , R5 A refrigerant such as 0 8B, R4 10A, hydrocarbon, carbon dioxide or ammonia is used in a scroll compressor for refrigeration and refrigeration. φ [Prior Art] The preferred pressure ratio in the refrigerating cycle system of the freezing machine is 4 to 20, and the refrigerating cycle system is a case where a scroll compressor is used, except that the scroll by the scroll compressor is increased. Other than the ratio of the volume at the time of completion of suction of the compression chamber formed by the body (vortex wrap) and the volume at the start of discharge (hereinafter referred to as design volume ratio), there is no other means for achieving such a pressure ratio. Moreover, it is difficult to increase the design volume ratio within a limited outer diameter in which the compressor cannot be enlarged. In Japanese Laid-Open Patent Publication No. Hei 7-27065 (hereinafter referred to as Patent Document 1), the basic vortex curve for forming the orbiting scroll wrap and the fixed scroll wrap is an algebraic spiral. This makes it possible to set the volume change rate, and since the volume change rate can be made larger by the round involute design, the performance can be improved to avoid a decrease in power due to insufficient compression of the refrigerant. [Patent Document 1] Japanese Laid-Open Patent Publication No. Hei 7-2 7065. SUMMARY OF THE INVENTION (Problems to be Solved by the Invention) -5- (2) 1273172 Patent Document 1 is useful for setting a volume change rate, and a scroll body Although the thickness (vortex thickness) of the winding start portion can be formed to be thicker than other portions, for example, in the device size equivalent to that of the conventional machine, reliability can be ensured, but the increase in the design volume ratio is not sufficiently reviewed. section. That is, Patent Document 1 discloses that, for example, when the dynamic diameter r, the off-angle 0, the coefficient of the algebraic spiral is a, and the index of the algebraic spiral is k, in the algebraic spiral curve of r = a 0 k (formula 1) The coefficient a of the change algebra spiral or the index k of the algebraic spiral increases the thickness of the wrap of the winding start portion of the wrap for increasing the pressure of the actuating fluid. Here, the reliability of the actuating fluid is to increase the thickness of the wrap of the winding start portion of the wrap, and to increase the pressure ratio without increasing the size of the device, thereby increasing the take-up angle of the wrap, that is, the wrapper does not The vortex is formed wide. In this case, the thickness of the wrap of the wrap body around the wrap and the wrap of the non-orbiting wrap is thinned at the end of the wrap having an increased yaw angle of zero. In particular, a scroll type # compressor in which an asymmetric scroll is formed is formed when the suction of the outermost peripheral portion of the wrap of the orbiting wrap and the inner peripheral wall of the non-orbiting wrap is completed, because The winding end portion of the orbiting wrap having a small scroll ring thickness is in contact with the wrap body (vortex ring) of the non-orbiting wrap, and reliability is a problem. Here, only the coefficient a of the algebraic spiral of the variation 1 or the index k of the algebraic spiral can not simultaneously increase the thickness of the scroll wrap at the end of the wrap, and increase the design volume ratio, and ensure reliability. SUMMARY OF THE INVENTION An object of the present invention is to provide a scroll compressor which can increase a design volume ratio for a scroll compressor having a scroll body and which has high reliability even under high pressure ratio operation. -6- (3) 1273172 (Means for Solving the Problem) The scroll compressor of the present invention for achieving the above object has a compression mechanism which uses an algebraic spiral curve represented by a polar coordinate form as A substantially vortex curve having a side shape formed by an envelope of the basic vortex curve is provided with a wrap wrap and a non-orbiting scroll which are erected to the end plate, and the wrap wrap and the non-wound wrap The scrolls of the orbiting scroll are fitted to each other in a state of being inwardly, so that the orbiting scroll wraps about Φ on the surface of the non-orbiting scroll to revolve at a predetermined radius, thereby reducing The volume of the fluid in the sealed space generated between the wraps of the two wraps is compressed, and at least the wrap of the wrap is included in the two wraps The basic vortex curve of the scroll body and the portion of the envelope are different in distance. As described above, the spiral body (winding wrap) and the non-wound body having the algebraic spiral curve as a basic vortex curve for forming a scroll body and the envelope of the basic vortex curve constitute the wrap wrap of the shape The wrap of the wrap (non-circular wrap), wherein at least the wrap of the wrap is a portion having a basic vortex curve of the wrap and a different distance of the envelope. According to this configuration, the scroll volume of the scroll body of the orbiting scroll can be arbitrarily changed to increase the design volume ratio, and the scroll compressor having high reliability under high pressure ratio operation can be provided. In particular, by intermeshing and combining the wrap body of the non-orbiting wrap and the wrap body around the wrap, a pair of closed spaces can be formed, which are inside and outside the wrap body around the wrap The inner volume at the time of completion of suction is that the retreating volumes are different from each other, that is, a so-called scroll compressor having an asymmetric scroll, in order to thicken the discharge side of the orbiting wrap, that is, the vortex at the beginning of the winding (4) When the thickness of the ring is 1273172 and the design volume ratio is increased, and the wrap body of the wrap wrap having a large take-up angle of the wrap is formed, the wrap angle can be increased without increasing the take-up angle of the wrap. Since the winding end portion of the scroll is wide, reliability can be ensured and the design volume ratio can be improved at the same time. Further, in the scroll compressor of the present invention, the portion of the spiral wrap of the orbiting wrap that has a different basic vortex curve and the envelope distance may be a wrap end portion including the wrap. In this case, even if the scroll thickness at the beginning of the winding φ is thicker than the other vortex thicknesses, the spiral body of the orbiting scroll is provided, and the volume of the spiral body with the algebraic spiral curve as the reference vortex curve The scroll thickness of the end portion is not required to be thin, and a scroll having a desired thickness from the start of winding to the end of winding can be obtained. Further, in the scroll compressor of the present invention described above, the distance between the basic vortex curve of the wrap of the orbiting wrap and the portion of the envelope having a different distance from the wrap may be longer than the other portions. In this case as well, even if the thickness of the scroll at the beginning of the winding is thicker than the thickness of the other vortex, the spiral body of the vortex is provided, and the spiral of the vortex is used as the reference vortex curve. The wrap thickness of the winding end portion is not required to be thin, and a wrap having a desired thickness from the start of winding to the end of winding can be obtained. Further, in the scroll compressor of the present invention described above, the basic vortex curve is an algebraic spiral curve, and the dynamic diameter is r, the yaw angle is 0, the coefficient of the algebraic spiral is a, and the index of the algebraic spiral is When k is used, it may be represented by r = a 0 k (Formula 1). In this case, the portion of the spiral vortex of the orbiting scroll and the distance between the basic vortex lines and the path of the wrap line may be different in an arbitrary yaw angle of the vortex body. It may be different from the range of the offset angle 0 within 3 6 0 (5) 1273172 degrees from the end portion of the scroll of the scroll. In this case, the spiral body (winding wrap) and the wrap of the fixed wrap (the wrap body) having the algebraic spiral curve as a basic vortex curve for forming the wrap body and the fixed wrap The basic vortex curve and the envelope distance constituting the outer wall surface (inner side wall surface) of the orbiting scroll are reduced (increased) by an arbitrary yaw angle 0. At the same time, in the yaw angle 0 of the inner wall surface (outer side wall surface) of the fixed scroll, and the same as the outer wall surface (the inner wall surface) of the orbiting wrap, the distance between the basic vortex curve and the φ envelope is increased (reduced) The part that is reduced (increased) around the wrap. Therefore, the vortex thickness of the orbiting scroll can be changed for any yaw angle 0, so that the two vortex bodies can be geometrically contacted. In particular, it may be different in a section from the vortex end portion of the scroll body to the yaw angle 0 within 360 degrees. Further, in the section from the arbitrary yaw angle 0 to the end of the winding outer spiral wall surface, the distance between the basic vortex curve and the envelope is used as the coefficient of the yaw angle 0, and the distance in the interval is gradually decreased. In the same section as the outer wall surface of the orbiting wrap, the distance between the basic vortex curve and the envelope is also increased in the same section as the outer wrap surface of the wrap wrap. Also as a coefficient of declination 0. Thereby, the thickness of the wrap around the wrap can be increased without greatly changing the outer diameter of the wrap. Further, in order to achieve the above object, the scroll compressor of the present invention has a compression mechanism including a wrap body which is a wrap wrap and an unwind wrap for the end plate, and the wrap wrap and The aforementioned scroll bodies of the non-orbiting scrolls are fitted to each other in a state of being inwardly, so that the aforementioned orbiting scrolls are subjected to a predetermined radius for a manner in which the non-orbiting scrolls do not rotate on the surface -9-(6) 1273172 The revolving motion is performed by reducing the volume of the fluid in the sealed space between the scrolls of the two wraps, and the outer side surface of the wrap of the wrap wrap is The inner side surface of the fixed scroll in the closed space, the inner side surface of the scroll body of the fixed scroll, and the aforementioned side surface between the outer side surfaces of the spiral body of the fixed scroll in which the scroll wrap is disposed The distance between the wraps of the fixed wrap is such that the distance between the outermost wraps is larger than the distance between the other wraps. By having such a configuration, the inter-vortex distance ratio of the wrap of the fixed wrap is made by the wrap around the wrap of the wrap and the outermost peripheral portion of the wrap of the fixed wrap. In the other sections, the distance between the scrolls is larger, and the wrap width of the winding end portion of the wrap wrap around the wrap is increased to be equal to or higher than that of other portions, and the reliability of the wrap wrap can be improved. And can improve the performance of the scroll compressor. Further, the scroll compressor to which the present invention is applied is used in a refrigerating machine of a refrigerating cycle system because the desired pressure ratio can be obtained only by the outer dimensions of a conventionally constant pressure φ retracting machine. Therefore, the field occupied by the refrigeration cycle system in the freezing machine can be formed larger than the field of non-frozen materials. (Effect of the Invention) According to the present invention, it is possible to provide a scroll compressor which can increase the design volume ratio and which has high reliability at high pressure ratio operation. [Embodiment] -10- (7) 1273172 Hereinafter, an embodiment of the present invention will be described with reference to Figs. 1 to 6 . Fig. 1 is a longitudinal sectional view showing a scroll compressor according to an embodiment of the present invention. The scroll compressor 11 is provided with a fixed scroll 3 that wraps around one of the wrap 1 and the non-orbiting wrap, a crank shaft 1 that rotates the wrap 1 , and a frame that supports the crank shaft 1 2 (3), the Audan ring 14 that allows the orbital motion of the wrap 1 and prevents the rotation motion, the motor 15 for driving the crankshaft, and the like. Here, the wraps of the two scrolls 1, 3 are formed according to the envelope φ line of the algebraic spiral curve. The algebraic spiral curve used in the present embodiment is the dynamic diameter r, the declination angle 0, the coefficient of the algebraic spiral is a, and the index of the algebraic spiral is k, which can be represented by r = a 0 k (formula 1). By determining the shape of each of the wraps 1 and 3 of the wrap by the curve of the basic vortex curve, the thickness of the wrap of the winding start portion of the wrapper having a high pressure of the actuating fluid is higher than that of the other. Partially larger, the number of rolls can be increased in the same area compared to the involute curve. By appropriately setting the coefficient a of the algebraic spiral of the formula 1 and the index k of the algebraic spiral, if the number of turns can be increased under the same area as compared with the involute curve, the thickness of the scroll of each of the scroll bodies φ 1 and 3 It gradually decreases toward the end of the winding. Here, by changing the distance between the envelope and the basic vortex curve by the angling angle, the shape of the vortex ring having an arbitrary yaw angle can be formed, and in particular, the thickness of the vortex ring is required to vary within the winding end portion. The desired shape can be obtained by the distance between the envelope and the basic vortex curve. The shape of the scroll bodies 1 and 3 will be described later. In the scroll compressor of such a configuration, the crank shaft 12 is rotated by energizing the motor 15, and the orbiting scroll 1 is not rotated by the Audon ring 14 to perform the revolving motion. The low-temperature low-pressure compressed fluid flowing from the suction pipe 16 is reduced by the volume of the closed space formed by the two scrolls 1, 3, and is compressed by -11 - (8) 1273172. Since the compressed fluid compressed in the sealed space becomes high temperature and high pressure, the compressed fluid of the low temperature liquid taken out from the refrigeration cycle flows into the compression chamber through the injection pipe 17, and becomes a compressed fluid of the gas when discharged during the compression process. The temperature will drop. The compressed fluid which has become a high temperature and a high pressure by the compression process is discharged from the discharge port 7 into the compression casing, passes between the components of the casing and the compressor in the casing, and is discharged from the discharge pipe 18 into the refrigeration cycle. Fig. 2 is a plan view showing a scroll shape of a scroll compressor according to an embodiment of the present invention. In Fig. 2, the wrap of the orbiting scroll (orbiting wrap) 2 is a vortex having a non-circular wrap around the outer wall surface 2 of the wrap wrap and the side wall surface 2i of the wrap wrap. The winding body (referred to as a fixed scroll body in this embodiment) 4 is provided with a fixed scroll outer wall surface 4〇 and a fixed scroll inner wall surface 4i. The fixed scroll 4 is erected on the fixed scroll end plate 5. The specific structure, such as the height of the tooth bottom surface 5a of the fixed scroll end plate 5 which is erected by the fixed scroll 4 which is in contact with the first end surface of the wrap around the wrap of the wrap, is a fixed wand The height of the end plates is different. In the case of this embodiment, the inner peripheral wall of the fixed scroll end 5 is continuous from the fixed scroll 4 and becomes a part of the inner wall surface 4i of the fixed scroll 4. As will be described in detail later, the portion a to b around the outer wall surface 2 of the wrap and the portion 'to b of the fixed scroll inner wall surface 4i' are between the basic vortex curve in this embodiment. The interval ε Η varies, that is, the portion of the thickness of the wrap around the wrap 2 has been increased. The angles of point a and point a' and point b and point b are the same. Point c' is the position at which the vortex end angle of the scroll on the fixed scroll body@side face 4i is reduced by only 36 degrees. The point c is the vortex at the same angle as the aforementioned point c. The outer wall of the roll is -12- (9) 1273172. The suction port 6 is an opening for supplying a fluid before being compressed. The discharge port 7 is a portion for the fluid to be compressed to flow out. In Fig. 2, the start angle of the start of the wrap around the orbiting scroll 2 and the fixed wrap 4 is rotated by 180 degrees and the center 0 of the fixed wrap 4 and the center of the wrap wrap 2 are fixed. 〇 'Intermeshing only by staggering the radius ε. Further, when the wrap 4 of the non-orbiting wrap 3 and the wrap 2 around the wrap 1 are meshed with each other, φ inhalation is formed on the inner side and the outer side of the wrap 2 around the wrap 1 The inner volume at the time of completion is a pair of closed spaces in which the retracting volumes are different from each other, and the orbiting scroll 2 and the fixed scroll 4 form an asymmetric scroll. Further, in the state of the orbiting scroll 2 and the fixed scroll 4 of Fig. 2, the state of the wrap is shown when the wrap end point e and the wrap angle are smaller than the point e (the angle Θ is small). The wound body 2 and the fixed scroll body 4 are in contact with each other, and a closed space between the outer peripheral wall surface 2 of the orbiting scroll and the side wall surface 4i of the fixed scroll body is formed, and the fluid suction is completed. The shape of the outer side wall surface 2 of the orbiting scroll and the side wall surface 4 i of the fixed Φ scroll body in Fig. 2 will be described using Fig. 3. The broken line 8 is a basic vortex curve for defining the shape of the outer wall surface 2 〇 of the wrap wrap and the inner curve 4i of the fixed wrap, and the dynamic diameter r, the yaw angle 0, and the coefficient a of the algebraic spiral are shown by the formula. When the exponent of the algebraic spiral is k, it becomes the formula r = a 0 k (formula 1). The broken line 9 is a basic vortex curve for defining the shape of the inner wall surface 2i of the scroll body and the curve 4' of the outer side of the fixed scroll body. The basic vortex curve shown by these two broken lines is to rotate the start angle of the start of the scroll by 180 degrees, and the winding start point is the same point 〇, which is indicated by a continuous broken line in Fig. 3. The point f on the outer wall surface 2 of the orbiting scroll and the point 上 on the side wall surface 4 i of the fixed scroll are the points on the wall corresponding to the point d of the figure -13-(10) 1273172 2 . The point g on the broken line 8 is a point on the basic vortex curve where the point f and the Γ become the same off angle. The point b on the outer wall surface 2 of the wrap around the wrap and the point b' on the inner wall surface 4 i of the fixed wrap are each a point on the wall surface corresponding to the point e of Fig. 2. The point i on the broken line 8 is a point on the basic vortex curve where the points b and b' become the same off angle. The same point h is a point on the basic vortex curve where point a and point a' become the same declination. § Fig. 3(a) is a vortex ring forming method showing a conventional technique disclosed in the patent document, and Fig. 3(b) is a vortex forming method showing the present embodiment. In Fig. 3(a), the outer wall surface 2 of the orbiting scroll with the dotted line 8 as the basic vortex curve is the inner side of the envelope indicated by the formula r = a 0 k+ ε Η (formula 2). In the curve, the fixed scroll inner wall surface 4i is formed by the outer curve only by ε ,, and the distance between each of the envelopes 2 〇 and 4 i is the turning radius ε (ie, ε = 2 丨 ε Η | ). Similarly, the dashed line 9 is used as the basic vortex curve of the wraparound inner wall side surface 2i, which is an envelope represented by the formula r = a 0 k + ε Η (formula 2) (but the dashed line 8 is deviated by 180 degrees). Among the lines, there is only the outer curve of e ,, and the outer side wall surface 4 固定 of the fixed scroll is a curve in which only ε Η becomes the inner side. The distance between the respective package paths 2i is the same as the winding radius ε which is the same as the distance between the wraparound scroll outer wall surface 2〇 and the fixed scroll inner wall surface 4i having the broken line 8 as a basic vortex curve. In the third diagram (b), the distance ε Η from the point a to the point b on the outer wall surface 2 〇 of the wrap wrap is changed by the distance ε Η as a coefficient of the declination 0, Let ε Η in Fig. 3(a) gradually become smaller, and at the end of the scroll -14-(11) 1273172, point b becomes ε H f . At the same time, the distance ε 与 from the dotted line 8 in the interval of the points a' to b' on the side wall surface 4 i of the fixed scroll body is increased as the portion which is reduced by the outer wall surface 2 of the orbiting scroll. The coefficient of the yaw angle 0 becomes ε 在 at the end point b' of the scroll, and the distance between the outer wall surface 2 of the wrap around the wrap and the side wall surface 4i of the fixed wrap is taken as the revolving radius. (ie, £=|£11 〖,|-丨ε H f | ). Thereby, the thickness of the wrap around the end of the wrap of the wrap 2 can be increased by only the difference of ε Η of the off-angle 0. • In Fig. 4, the relationship between the envelope ε Η and the yaw angle of the basic vortex curve showing the envelope of the outer wall surface of the wrap wrap and the envelope of the fixed scroll inner wall surface 4 i is shown. An example. The line 19 in the figure is a change showing the distance ε Η of the outer wall surface 2 绕 of the orbiting scroll and the basic vortex curve, that is, the broken line 8 in the present embodiment, and the line 20 is the side wall surface of the fixed scroll in the present embodiment. 4i and the basic vortex curve are also the changes of the distance ε Η of the dotted line 8. And the dotted line 2 1 is the distance ε Η of the prior art. From the wrap start angle 0 0 to the declination 0 a, it is a certain 値 ε Η, and the yaw angles 0 a to 0 b are intervals in which the 0 basic eddy curve and the envelope distance change in the present embodiment. Line 19 and line 20 are the off-angles of the line 21 (the coefficient formula of the same as the line 21). Fig. 4 (a) shows the case where the distance between the basic vortex curve and the envelope changes with the primary coefficient of the declination 0. Fig. 4(b) shows the case where the distance of the basic vortex curve of the yaw angle 0c is the change rate of the line 19 and the line 20 which are ε Ht and ε Ht', respectively, and can also be changed by the second order coefficient. The method of changing the section, etc. Next, the case where the thickness of the scroll wrap around the wrap 2 is increased by the above method, and the conventional technique is that only the algebra-15-(12) 1273172 spiral is used. The design volume ratio of the coefficient a and the exponent k of the algebraic spiral is different. Fig. 5(a) shows the use of the present embodiment, and Fig. 5(b) shows the use of the prior art to increase the orbiting vortex. When the wrap 2 of the wrap 2 ends the thickness of the wrap, respectively, it is shown that the wraparound scroll body 2 is the same outer diameter r and the same wrap ends the wrap thickness T when the wrap around the outer wall surface of the wrap 2 The sealed space l〇a formed by the fixed scroll inner wall surface 4i is a plan view showing a state in which fluid intake is completed. And FIGS. 5(c) and 5(d) are diagrams showing the positional relationship between the orbiting scroll and the fixed scroll when the arbitrary angle revolving motion is performed in FIG. 5(a) and (b), by winding The outer wall surface 2 of the whirling scroll and the closed space 1 〇b formed by the side wall surface 4i of the fixed scroll body are shown in the two figures before the same diameter, that is, the state where the discharge port 7 is turned on. The design volume ratio is the closed space 10a. And the ratio of the closed space l〇b, when the height of the scroll of the two scroll bodies is constant from the start of the scroll to the end of the scroll, it means that the sealed spaces 10a and 10b are projected onto the orbiting scroll end plate or Φ The ratio of the area when the scroll end plate is fixed. The broken lines 8a to 8d in the figure are the basic vortex curves of the outer wall surface 2 of the orbiting scroll and the side wall surface 4i of the fixed scroll formed by the closed spaces l〇a and 10b. The area around the outer wall surface of the orbiting wrap is drawn. Here, the area of the closed space is explained. As can be seen from Fig. 3(a), the area of the closed space l〇a is the point g to the point i of the broken line 8. The product of the length and the radius of revolving ε is almost equal. Similarly, the area of the confined space in Fig. 5 is different and virtual. The product of the lengths of the lines 8a to 8d and the radius of revolving ε is almost equal. Thereby, the comparison of the design volume ratios is made by comparing the lengths of the basic vortex curves for forming the respective sealed spaces. - (13) 1273172 Fig. 6 is a graph comparing the lengths of the broken lines 8a to 8d of Fig. 5. In the figure, the length 1 is the length indexed by the length of the broken line 8a, and the length 2 is the dotted line 8b indicating the broken line 8a. Similarly, the length 3 is the length in which the length of the broken line 8c is indexed, and the length 4 is the ratio indicating the length of the broken line 8d for the broken line 8c. According to the present embodiment, it is understood that when the thickness of the vortex ring is increased The design volume ratio is larger than the design volume ratio of the prior art. By the above embodiment, it is possible to achieve an enlargement of the design volume ratio when the winding wrap is increased by the same outer diameter of the wrap. Further, the refrigerating and refrigerating machine of the refrigerating cycle system is almost the same as the refrigerating and refrigerating machine in which the scroll compressor having the increased pressure ratio applied to the present invention is composed of the scroll member having the same size as the conventional one. The high pressure ratio can be obtained without changing the size of the conventional refrigerating cycle, and the operation with high reliability and high efficiency can be ensured. As described so far, the algebraic spiral curve is used as the basic vortex curve of the scroll body according to the embodiment of the present invention, and the basic vortex which will form and wrap the outer wall surface of the wrap body and the side wall surface of the fixed scroll body The distance between the envelope of the curve and the basic vortex curve is changed as the coefficient of the declination of the algebraic spiral, even if the outer diameter of the orbiting scroll is the same and the thickness of the scroll wrap is the same as that of the other part. An enlargement of the design volume ratio can also be achieved if the thickness is slightly the same. Thereby, the reliability of the end of the scroll wrap can be ensured and the increase of the illustrated power due to the insufficient compression of the high pressure ratio during operation can be prevented and the efficiency can be improved. BRIEF DESCRIPTION OF THE DRAWINGS [Fig. 1] A longitudinal section of a scroll compressor according to an embodiment of the present invention -17-(14) 1273172. Fig. 2 is a plan view showing a wrap of a scroll compressor according to an embodiment of the present invention. [Fig. 3] A method of constructing a wrap of a scroll compressor according to an embodiment of the present invention. Fig. 4 is a graph showing the distance between the basic vortex curve and the envelope of the scroll wall surface according to an embodiment of the present invention. p [Fig. 5] An embodiment of the present invention and the orbiting scroll and the fixed scroll formed by the prior art are compared with the outer wall surface of the orbiting scroll and the side wall surface of the fixed scroll. The sealed space is a plan view of the state before the fluid intake is completed and before the discharge. [Fig. 6] A graph comparing the lengths of the basic vortex curves in Fig. 5. [Description of main component symbols] 1 : Winding wrap 2: Winding wrap 2i: Wrap around the inner wall surface of the wrap 2: Wrap around the outer wall surface of the wrap: Fixed wrap (non-wound wrap) 4: fixed scroll body 4 i ·_ fixed scroll body side wall surface (curve) 40 : fixed scroll body outer curve 5 · fixed scroll end plate 5a : tooth bottom surface -18- (15) 1273172 6 : suction port 7: discharge port 8: basic vortex curve 8 a : broken line 8 b . broken line 8 c. broken line 8 c : broken line 8 d · broken line 9 : broken line 1 0 : closed space 1 0 a : closed space l 〇 b : closed space 1 1 : Scroll compressor 1 2 : Crankshaft 13 : Frame (frame) φ 1 4 : Ou Dan ring 1 5 : Motor 1 6 : Suction piping 1 7 : Injection piping 1 8 : Discharge piping 19 : Line 20 : Line 21 · Dotted line -19