200521328 (1) 九、發明說明 【發明所屬之技術領域】 本發明是關於是爲一種容積形流體機械的渦卷式壓縮 機，特別是關於工作流體爲使用 R404A、R5 0 7A、 R5 0 8B、R4 10A、碳化氫、二氧化碳、氨等低溫用冷媒的 冷凍冷藏用上所使用的渦卷式壓縮機。 【先前技術】 於冷凍用機器的冷凍循環中壓力比是形成爲4〜20, 因於以習知的基本渦曲線爲圓漸開線的渦旋體中容積變化 率是爲一定，所以爲了使渦旋體所形成的壓縮室的吸入結 束時的容積和吐出開始時的容積的比（以下稱設計容積 比）能夠應對於所需要的壓力比，其解決手段除了加大渦 旋體的卷角，使渦旋體外徑變大以外沒有其他手段，因此 要在所局限的外徑範圍內來增加設計容積比是有所困難。 於日本特開平7-27065號公報（以下稱專利文獻1 ) 中，是對可構成旋繞渦卷渦捲體及固定渦捲渦旋體的基本 渦曲線使用代數螺線。藉此使容積變化率的設定成爲可 能，由於其與以圓漸開線來設計時的狀況相比是能夠使容 積變化率變大，所以能夠實現因冷媒的不完全壓縮所形成 的指示功率的降低來造成性能提昇。 另一方面，就其擴徑區間形成有密閉空間的技術而 言，於日本特開昭56-2070 1號公報（以下稱專利文獻 2 )中，是以旋繞渦卷渦旋體的外側壁面當中卷尾部的 -5- 200521328 (2) 1 8 0度區間與固定渦卷渦旋體來形成密閉空間以做爲起動 室。接著是將固定渦卷渦旋體內側壁面的卷尾位置延長形 成爲是與旋繞渦卷渦旋體的外側壁面爲大致同一位置。 藉此使其與固定渦卷的渦旋體未延長的習知構成相 比，是可不需固定渦卷渦旋體內側壁面的擴徑加工就能夠 縮小外徑，經由旋繞渦卷的渦旋體外側壁面和固定渦卷的 渦旋體內側壁面所形成的最大密閉空間的擴大就可降低同 一行程容積的渦旋體的高度。 【專利文獻1】日本特開平07-27065號公報 【專利文獻2】日本特開昭56-20701號公報 【發明內容】 〔發明欲解決之課題〕 但是專利文獻1的旋繞渦卷及固定渦卷，是以卷首開 始角度爲錯開1 80度的狀態互相嚅合，卷尾偏角0是形成 爲相同。此外這2個渦卷的卷尾位置是形成爲在互相錯開 1 8 0度的位置上。 因此，從其旋繞渦卷渦旋體的外側壁面的卷尾位置起 與1 8 0度區間成相向的固定渦卷渦旋體的內側壁面是有必 要朝徑方向外方擴徑。於需要擴大該徑的區間，並未形成 可成爲壓縮室的密閉空間，反而造成設計容積比的損失。 於專利文獻2中，旋繞渦卷的渦旋體外側壁面和固定 渦卷的渦旋體內側壁面所形成的密閉空間的設計容積比， 是因爲在端板設有流體通道，或削除旋繞渦卷渦旋體的卷 200521328 (3) 始部，使其與旋繞渦卷的渦旋體外側壁面和固定渦卷的渦 旋體內側壁面所形成的密閉空間幾乎是成相等，所以固定 渦卷渦旋體卷尾位置的延長並未達成設計容積比的增加。 這些以習知技術所獲得的設計容積比，有時要做爲所 欲搭載的機器例如冷凍用機器中需要的高壓力比所應對的 設計容積比是顯不足。於該狀況時，壓縮只會運作至需要 壓力的途中形成不完全壓縮。 此外就如冷凍循環上使用碳化氫類冷媒時的更高壓力 比的運轉條件下而言，會有不完全壓縮所形成的指示功率 增加而造成性能降低的問題。 本發明的目的，是提供一種渦旋體外徑是爲相同的原 尺寸就可增加設計容積比，於高壓力比運轉時具高效率的 渦卷式壓縮機。 〔用以解決課題之手段〕 爲達成上述目的，是於本發明的渦卷式壓縮機中，具 有以基本渦曲線爲代數螺線曲線所構成的旋繞渦卷渦旋體 及固定渦卷渦旋體，將可構成爲上述固定渦卷的渦旋體內 側壁面的曲線卷尾位置延長成是位於可構成上述旋繞渦卷 的渦旋體外側壁面的曲線卷尾位置附近，並且是將可構成 爲上述旋繞渦卷渦旋體及上述固定渦卷渦旋體的基本渦曲 線的中心對上述旋轉及固定渦卷的端板中心，是形成爲錯 開在大致從上述渦旋體卷尾位置起連接基本渦曲線中心的 直線方向。 200521328 (4) 藉此在端板是爲相同外徑的原尺寸狀況下，就可擴大 最大密閉空間的容積以達到設計容積比的增加。 此外，以旋繞渦卷的外側及內側2個密閉空間是同時 導通於吐出埠爲佳。 另外，爲了改善導通時的壓力不平衡以減少在2個密 閉空間內的浅漏’最好是於設計容積比小的旋繞渦卷渦旋 體內側壁面和固定渦卷渦旋體外側壁面所形成的密閉空間 上開口成較長的位置設有液噴射流入口。 〔發明效果〕 根據本發明時，於高壓力比運轉時能夠防止不完全壓 縮所形成的指示功率的增加，又能夠防止壓縮室間的內部 洩漏以提昇效率。 【實施方式】 〔發明之最佳實施形態〕 以下，是根據第1圖至第6圖來說明本發明的實施 例。 於第1圖中，圖示本發明一實施形態所應用的渦卷壓 縮機縱剖面圖。渦卷式壓縮機13，具備有：旋繞渦卷1 和固定渦卷3 ;可使旋繞渦卷1進行旋轉的曲柄軸14 ;對 曲柄軸14進行支撐的框架15;可防止旋繞渦卷1的自轉 但容許旋繞渦卷1公轉運動的歐丹環16;及，可驅動曲 柄軸14的馬達17。兩渦卷1、3的渦旋體，是以可成爲 -8 - 200521328 (5) 其渦旋形狀規定基準曲線的基本渦曲線爲代數螺線曲線。 將固定渦卷3的渦旋體偏角形成爲要比旋繞渦卷1的渦旋 體偏角還大約180度，使固定渦卷3的卷尾位置得以延長 成是與旋繞渦卷1的卷尾位置爲同等以上的位置，使固定 渦卷3的內側壁面和旋繞渦卷1的外側壁面所形成的密閉 空間成擴大形狀。 接著，對如此所構成的渦卷式壓縮機的壓縮過程進行 說明。藉由對馬達1 7進行通電使曲柄軸1 4進行旋轉，旋 繞渦卷1是由歐丹環16使其形成不會自轉但是會進行公 轉運動。藉由旋繞渦卷1的公轉，使從吸入管1 8流入的 低溫低壓被壓縮流體，因兩渦卷1、3所形成的密閉空間 容積變小而受到壓縮。在該密閉空間內受到壓縮的被壓縮 流體因是形成爲高溫高壓，所以是藉由噴射管19使在壓 縮行程的途中利用冷凍循環所取出的低溫被壓縮流體流入 壓縮室內以降低吐出時的氣體被壓縮流體的溫度。流入在 壓縮室內的液狀被壓縮流體的量，以是爲要在壓縮室內進 行氣體化的量爲佳。經過如此壓縮行程而成爲高溫高壓的 被壓縮流體，是從吐出埠7排出至壓縮機殼內，然後通過 機殼和機殼內的壓縮機構成零件之間，從吐出管20排往 冷凍循環內。 使用第2圖對旋繞渦卷1和非旋繞渦卷3的渦旋體進 行說明。旋繞渦卷的渦旋體2，其渦旋形狀是受旋繞外側 曲線2〇和旋繞內側曲線2i的規定。另外，固定渦卷的渦 旋體4，其渦旋形狀是受固定外側曲線4〇和固定內側曲 -9- 200521328 (6) 線4 i的規定。該固定渦旋體4 ’ ϊ彳固疋渦卷板5是形成 爲直立著。固定渦旋體4形狀規定的基本渦曲線的中心 〇’ ，是對固定渦卷端板5的中心0’形成爲錯開配置在 從固定渦旋體4的卷尾起連接著固定渦卷端板5中心的方 向，以在端板5內能夠擴大形成有渦旋體4的占有範圍。 固定外側曲線4〇當中，a至b的部份是爲本發明上述固 定渦旋體的延長部，藉由卷尾偏角0是增加約180度，使 卷尾位置b得以是位於上述旋繞渦旋體2的卷尾位置附 近。於固定渦卷3的一部份設有：壓縮前的流體流入用的 吸入埠6和壓縮後的流體流出用的吐出璋7，及設置在固 定渦卷端板5的液噴射流入口 8。 該液噴射流入口 8，於本實施形態中，是配置成靠近 固定外側曲線4〇並且是配置在不導通於吸入埠及吐出埠 的位置上。 於此，旋繞渦旋體2及固定渦旋體4構成用的基本渦 曲線，是爲代數螺線曲線，爲了使卷始部的渦旋壁厚成爲 更厚，是只將卷始部的偏角0區間的代數螺線的係數a或 者代數螺線的指數k的値形成爲較大，這以外的區間的代 數螺線的係數a或者代數螺線的指數k的値是形成爲一 定。如此是由修正後的基本渦曲線的包絡線來構成旋繞渦 旋體2及固定渦旋體4的內側曲線及外側曲線。 於第6圖中，圖示使用外徑是爲相同的昔知技術和本 發明的旋繞及固定渦卷時的壓力比的比較。系列1是表示 習知技術下的壓力比，系列2是表示以基本渦曲線爲代數 -10- 200521328 (7) 螺線時的壓力比，系統3是表示以基本渦曲線爲代數螺線 使端板中心和基本渦曲線的中心爲偏心時的壓力比，系列 4是表示包括有本發明全國部發明要素時的壓力比。根據 本實施例可提供一種在有限外徑範圍內的高壓比用渦旋 體。另外，藉此使旋繞渦旋體2及固定渦旋體4的渦旋壁 厚度都能夠從渦旋的卷首開始朝卷尾連續性進行變化，由 於是將內部流體壓力爲最高壓的渦旋體的中央部形成爲較 厚因此能夠提昇可靠度，降低內部洩漏。 第3圖，是表示本發明一實施形態相關的渦卷式壓縮 機的渦旋體所進行的壓縮行程平面圖。按照第 3圖 (a )、第3圖（b )、第3圖（c )的順序，表示僅任意 角度進行公轉運動時的旋繞渦卷和固定渦卷的位置關係。 第3圖（a )是表示旋繞外側曲線2〇和固定內側曲線4i 所形成的密閉空間9a於流體吸入結束時的狀態。第3圖 (b )是表示從第3圖（a )的狀態大約僅進行了 1 80度公 轉運動後的狀態。於第3圖（b)中圖號10b是表示旋繞 內側曲線2i和固定外側曲線4〇所形成的密閉空間且是流 體吸入結束時的狀態。旋繞外側曲線2 〇和固定內側曲線 4i所形成的密閉空間9b，是表示從第3圖（a )的狀態開 始已有壓縮作用的狀態，其具有與密閉空間1 〇b相同的容 積。 第3圖（c )是表示從第3圖（b )的狀態僅進行了某 角度公轉運動的狀態。旋繞外側曲線2〇和固定內側曲線 4i所形成的密閉空間9c與旋繞內側曲線2i和固定外側曲 -11 - 200521328 (8) 線4〇所形成的密閉空間1 〇c，是爲相同容積。當從第3 圖（c )的狀態持續進行公轉運動時，2個密閉空間9 c、 l〇c會幾乎同時導通於吐出埠7。 於此，第3圖（b )中旋繞內側曲線2i和固定外側曲 線4〇所形成的密閉空間1 〇b，具有與固定渦旋體4的延 長部是形成爲無關的Vs’體積。此外，密閉空間9b可視 爲是由固定外側曲線4〇的卷尾位置爲a的固定渦旋體內 側曲線和旋繞內側曲線2i所形成的流體吸入結束時的狀 態，密閉空間9b的容積是形成爲與密閉空間1 Ob相同的 容積Vs’ 。相對於密閉空間9b的容積Vs’ ， 第3圖 (a )中旋繞外側曲線2〇和卷尾位置延長至b的固定內側 曲線4i所形成的密閉空間9a在流體吸入結束時的容積 V s是較大。第3圖（a )和第3圖（b )所示的旋繞外側 曲線2〇和固定內側曲線4i所形成的上述2個密閉空間9a 和9b邊受壓縮作用邊導通於吐出埠7時的容積，均是形 成爲如第3圖（c )所示的密閉空間9c的容積Vd。 因此，藉由將固定側渦旋體4的內側曲線4i的卷尾 位置從a延長至b是可使旋繞外側曲線2〇和固定內側曲 線4i所形成的密閉空間的內部容積比增加。但是，在第3 圖（a )所形成的密閉空間9a和在第3圖（b )所形成的 密閉空間l〇a都是在邊受壓縮作用的同時於成爲第3圖 (c )所示的密閉空間9c和10c時的內部壓力是成爲不 同，因此兩空間的壓力壓將會造成內部洩漏的原因。 因此藉由將壓縮機冷卻用的液噴射流入口 8如第1 .圖 200521328 (9) 所示配置在是靠近固定外側曲線4〇並且是不導通於吸入 璋6和吐出璋7的位置，是可使旋繞內側曲線2i和固定 外側曲線4〇所形成的密閉空間內有較多的被壓縮流體流 入，可使密閉空間的壓力上昇。於第4圖（a )至第4圖 (d)中，圖示著旋繞渦旋體2和固定渦旋體4所形成的 .密閉空間與液噴射流入口 8進行導通的狀態。 此外，第5圖是表示具有相同外徑的習知技術和本發 明的旋繞和固定渦旋體所形成的密閉空間內的曲柄角相對 於壓力變化的圖表。第4圖（a)是表示本發明的旋繞外 側曲線2〇和固定內側曲線4i所形成的密閉空間爲正要導 通於液噴射流入口 8之前的狀態，第4圖（b)是表示上 述密閉空間與液噴射流入口 8是形成爲不相關的瞬間狀 態。同樣地，第4圖（c )是表示本實施例的旋繞內側曲 線2i和固定外側曲線4 〇所形成的密閉空間爲正要導通 於液噴射流入口 8之前的狀態’及第4圖（d )是表示與 液噴射流入口 8是形成爲不相關的瞬間狀態。於第5圖 中，縱軸是表示壓力比，橫軸是表示曲柄角，曲線21是 表示本發明的旋繞和固定渦旋體的旋繞外側曲線2 〇和固 定內側曲線4i所形成的密閉空間的壓力變化，曲線22是 表示繞內側曲線2i和固定外側曲線4〇所形成的密閉空間 的壓力變化，曲線23是表示習知技術的密閉空間的壓力 變化。 於第5圖中，表示本發明機壓力變化的曲線2 1和2 2 的壓縮開始點形成爲是相差〗80度的原因是因爲固定內側 -13- 200521328 (10) 壁面經延長後所獲得的效果。此外，表示本發明機密閉空 間的壓力變化的曲線2 1和表示習知機密閉空間的壓力變 化的曲線23的壓縮作用開始的曲柄角爲不同的原因是， 因爲根據本發明延長了固定內側壁面後所獲得的效果及旋 繞和固定渦旋體的卷角是爲增加的原故。曲線21上的曲 柄角c、d，是分別應對在第4圖（a )、第4圖（b ) 中，曲線22上的曲柄角e、f，是分別應對在第4圖 (c)、第4圖（d)中。這2個密閉空間內的壓力，是於 曲柄角從c至d，從e至f的區間藉由從液噴射口流入的 被壓縮流體的流入使其壓力上昇變大。 再加上如曲柄角所示，2個密閉空間會因液噴射口開 口時間的不同造成不同的壓力上昇，因此對於設計壓力小 的密閉空間使其具有長的開口就能夠使曲柄角f的壓力成 爲是與設計壓力大的密閉空間內的壓力相同。如此一來第 3圖（c )的密閉空間1 0c的壓力會上昇，但密閉空間9c 的內部壓力並不會降低，所以就能夠緩和上述2個密閉空 間9c、1 0c的吐出埠7導通時的壓力不平衡，以達到降低 內部洩漏。 【圖式簡單說明】 第1圖爲本發明一實施形態的渦卷式壓縮機的渦旋部 平面圖。 第2圖爲本發明渦卷式壓縮機剖面圖。 第3圖爲表示本發明渦卷式壓縮機渦旋體的壓縮行程 -14- 200521328 (11) 平面圖。 第4圖爲表示本發明渦卷式壓縮機渦旋體的密閉空間 和液噴射流入口的導通狀態平面圖。 第5圖爲表示本發明及習知技術的曲柄角和壓力的圖 · 表。 - 第6匱|胃表示本發明及習知技術的曲柄角和壓力的圖 表。 【主要元件符號說明】 1 :旋繞渦卷 2 =旋繞渦旋體 3 :固定渦卷 4 :固定渦旋體 5 :固定渦卷端板 6 :吸入埠 7 :吐出埠 | 8 :液噴射流入口 18 :吸入管 1 9 :噴射管 20 :吐出管 -15-200521328 (1) IX. Description of the invention [Technical field to which the invention belongs] The present invention relates to a scroll compressor for a volumetric fluid machine, and particularly to working fluids using R404A, R5 0 7A, R5 0 8B, R4 10A, scroll compressor for refrigeration and refrigeration of low temperature refrigerants such as hydrocarbons, carbon dioxide and ammonia. [Prior art] The pressure ratio in the refrigerating cycle of a refrigerating machine is formed to 4 to 20, because the volume change rate in a vortex with a conventional basic vortex curve as a circular involute is constant, so in order to make The ratio of the volume of the compression chamber formed by the scroll body at the end of suction and the volume at the beginning of discharge (hereinafter referred to as the design volume ratio) can respond to the required pressure ratio. The solution is to increase the scroll angle of the scroll body. There is no other way to increase the outer diameter of the scroll body, so it is difficult to increase the design volume ratio within the limited outer diameter range. In Japanese Patent Application Laid-Open No. 7-27065 (hereinafter referred to as Patent Document 1), an algebraic spiral is used for a basic vortex curve that can constitute a spiral scroll scroll body and a fixed scroll scroll body. This makes it possible to set the volume change rate. Since the volume change rate can be made larger than when it is designed with a circular involute, it is possible to realize the indicated power due to incomplete compression of the refrigerant. Reduce to improve performance. On the other hand, in the technique of forming a closed space in the enlarged diameter section, in Japanese Patent Application Laid-Open No. 56-2070 1 (hereinafter referred to as Patent Document 2), the outer wall surface of the spiral scroll body -5- 200521328 (2) 180 ° section of the tail of the scroll and fixed scroll scroll to form a closed space as the starting chamber. Next, the position of the tail end of the inner wall surface of the fixed scroll scroll is extended to be substantially the same as the outer wall surface of the spiral scroll scroll. As a result, compared with the conventional structure in which the scroll body of the fixed scroll is not extended, the outer diameter can be reduced without the need to expand the inner wall surface of the fixed scroll body. The enlargement of the maximum enclosed space formed by the outer wall surface and the inner wall surface of the scroll inside the fixed scroll can reduce the height of the scroll with the same stroke volume. [Patent Document 1] Japanese Patent Laid-Open No. 07-27065 [Patent Document 2] Japanese Patent Laid-Open No. 56-20701 [Summary of the Invention] [Problems to be Solved by the Invention] However, the spiral scroll and fixed scroll of Patent Document 1 The angles at the beginning of the roll are staggered by 180 degrees, and the offset angle 0 at the end of the roll is formed to be the same. In addition, the end positions of the two scrolls are formed at positions 180 degrees apart from each other. Therefore, it is necessary to expand the diameter of the inner side wall surface of the fixed scroll scroll facing the 180 degree interval from the winding tail position of the outer side wall surface of the orbiting scroll scroll body. In the section where the diameter needs to be enlarged, a closed space that can become a compression chamber is not formed, but the design volume ratio is lost. In Patent Document 2, the design volume ratio of the closed space formed by the outer wall surface of the outer scroll surface of the swirling scroll and the inner wall surface of the inner scroll body of the fixed scroll is because the end plate is provided with a fluid passage, or the swirling scroll is removed The scroll volume of the scroll body 200521328 (3) The beginning of the scroll is almost equal to the closed space formed by the outer wall surface of the scroll body and the inner wall surface of the fixed scroll body, so the fixed scroll The extension of the body curl tail position did not reach the increase of the designed volume ratio. These design volume ratios obtained by conventional techniques are sometimes insufficient to cope with the high pressure ratios required for the equipment to be mounted, such as refrigeration equipment. In this situation, compression will only work until incomplete compression is formed on the way that requires pressure. In addition, under the operating conditions of higher pressure ratios such as when a hydrocarbon-based refrigerant is used in a refrigeration cycle, there is a problem that performance increases due to an increase in the indicated power due to incomplete compression. The object of the present invention is to provide a scroll compressor which can increase the design volume ratio when the outer diameter of the scroll body is the same as the original size, and has high efficiency when operating at a high pressure ratio. [Means for Solving the Problems] In order to achieve the above-mentioned object, the scroll compressor of the present invention includes a spiral scroll scroll body composed of a basic scroll curve as an algebraic spiral curve and a fixed scroll scroll. The curly tail position of the inner wall surface of the scroll body that can be configured as the fixed scroll is extended to be near the curly tail position of the outer wall surface of the scroll body that can constitute the spiral scroll. The center of the basic vortex curve of the orbiting scroll vortex body and the fixed scroll vortex body is formed so as to be connected to the center of the end plate of the orbiting scroll and fixed scroll staggered from the position of the scroll body tail. The straight direction of the center of the vortex curve. 200521328 (4) In this way, under the condition that the end plates have the same outer diameter, the volume of the maximum enclosed space can be enlarged to increase the design volume ratio. In addition, it is preferable that the two closed spaces outside and inside of the spiral scroll are connected to the discharge port at the same time. In addition, in order to improve the pressure imbalance during conduction and reduce the shallow leakage in the two confined spaces, it is best to be formed on the inner wall surface of the spiral scroll scroll body with a small volume ratio and the outer wall surface of the fixed scroll scroll body. The closed space of the opening is provided with a liquid jet flow inlet at a longer position. [Effects of the Invention] According to the present invention, it is possible to prevent an increase in the indicated power due to incomplete compression during high pressure ratio operation, and to prevent internal leakage between the compression chambers to improve efficiency. [Embodiment] [Best Embodiment of the Invention] Hereinafter, embodiments of the present invention will be described with reference to Figs. 1 to 6. Fig. 1 is a longitudinal sectional view of a scroll compressor to which an embodiment of the present invention is applied. The scroll compressor 13 includes: a scroll scroll 1 and a fixed scroll 3; a crank shaft 14 capable of rotating the scroll scroll 1; a frame 15 supporting the crank shaft 14; Ondan ring 16 which rotates but allows revolution of orbiting scroll 1; and motor 17 which can drive crankshaft 14. The scroll bodies of the two scrolls 1 and 3 are algebraic spiral curves based on the basic vortex curve that can become the reference curve of the vortex shape. The deflection angle of the scroll body of the fixed scroll 3 is formed to be about 180 degrees more than the deflection angle of the scroll body of the winding scroll 1, so that the position of the tail of the fixed scroll 3 can be extended to be the same as that of the winding scroll 1 The tail positions are equal or more, and the closed space formed by the inner side wall surface of the fixed scroll 3 and the outer side wall surface of the spiral scroll 1 is enlarged. Next, the compression process of the scroll compressor thus constructed will be described. The crank shaft 14 is rotated by energizing the motor 17, and the orbiting scroll 1 is formed by the ondan ring 16 so that it does not rotate, but performs a revolving motion. By orbiting the orbiting scroll 1, the low-temperature and low-pressure compressed fluid flowing from the suction pipe 18 is compressed because the volume of the closed space formed by the two scrolls 1 and 3 becomes small. Since the compressed fluid compressed in this closed space is formed at high temperature and high pressure, the low-temperature compressed fluid taken out by the refrigeration cycle during the compression stroke is flowed into the compression chamber through the injection pipe 19 to reduce the gas at the time of discharge. The temperature of the compressed fluid. The amount of the liquid compressed fluid flowing into the compression chamber is preferably the amount to be gasified in the compression chamber. After such a compression stroke, the compressed fluid that has become high temperature and high pressure is discharged from the discharge port 7 into the compressor casing, and then is discharged from the discharge pipe 20 into the refrigeration cycle through the casing and the compressor components in the casing. . The scroll bodies of the spiral wrap 1 and the non-scroll wrap 3 will be described using FIG. 2. The vortex body 2 of the spiral scroll is defined by the spiral outer curve 20 and the spiral inner curve 2i. In addition, the vortex shape of the fixed scroll scroll 4 is defined by the fixed outer curve 40 and the fixed inner curve -9- 200521328 (6) line 4 i. This fixed scroll body 4 'is a solid scroll plate 5 formed so as to stand upright. The center 0 ′ of the basic vortex curve defined by the shape of the fixed scroll 4 is formed so as to be offset from the center 0 ′ of the fixed scroll end plate 5 and is connected to the fixed scroll end plate from the end of the fixed scroll 4 5 in the direction of the center so that the occupation range in which the scroll body 4 is formed in the end plate 5 can be enlarged. Among the fixed outer curve 40, a to b are extensions of the above-mentioned fixed scroll body of the present invention. The curling angle 0 is increased by about 180 degrees, so that the curling position b can be located in the winding vortex. Near the tail end position of the spin body 2. A portion of the fixed scroll 3 is provided with a suction port 6 for fluid inflow before compression and a discharge port 7 for fluid outflow after compression, and a liquid jet flow inlet 8 provided in the end plate 5 of the fixed scroll. This liquid jet inlet 8 is arranged near the fixed outer curve 40 in the present embodiment and is arranged at a position where it is not conducted to the suction port and the discharge port. Here, the basic vortex curve for forming the swirling scroll body 2 and the fixed scroll body 4 is an algebraic spiral curve. In order to make the vortex wall thickness at the beginning of the roll thicker, only the deviation of the beginning of the roll is deviated. The coefficient a of the algebraic spiral or the index k of the algebraic spiral in the interval of angle 0 is formed to be relatively large. The coefficient a of the algebraic spiral or the index k of the algebraic spiral in the other intervals is formed to be constant. In this way, the inside curve and the outside curve of the swirling scroll body 2 and the fixed scroll body 4 are constituted by the envelope of the corrected basic vortex curve. Fig. 6 shows a comparison of the pressure ratios of the conventional technology using the same outer diameter and that of the spiral and fixed scroll according to the present invention. Series 1 is the pressure ratio under the conventional technique, Series 2 is the pressure ratio when the basic vortex curve is used as algebra -10- 200521328 (7) Pressure ratio when the spiral is used, and System 3 is the pressure ratio when the basic vortex is used as the algebraic spiral. The center of the plate and the center of the basic vortex curve are the pressure ratios when eccentric. Series 4 shows the pressure ratios when the invention elements of the whole country are included. According to this embodiment, it is possible to provide a scroll body for a high pressure ratio within a limited outer diameter range. In addition, the thickness of the scroll wall of the swirling scroll body 2 and the fixed scroll body 4 can be continuously changed from the beginning of the scroll to the end of the scroll. This is because the scroll body has the highest internal fluid pressure. The central part is thicker, which improves reliability and reduces internal leakage. Fig. 3 is a plan view showing a compression stroke performed by a scroll body of a scroll compressor according to an embodiment of the present invention. In the order of Fig. 3 (a), Fig. 3 (b), and Fig. 3 (c), the positional relationship between the spiral scroll and the fixed scroll when the revolution is performed at an arbitrary angle is shown. FIG. 3 (a) shows the state of the closed space 9a formed by winding the outer curve 20 and the fixed inner curve 4i at the end of the fluid suction. Fig. 3 (b) shows the state after the revolution of approximately 80 degrees from the state of Fig. 3 (a). In Fig. 3 (b), reference numeral 10b shows a closed space formed by winding the inner curve 2i and the fixed outer curve 40, and is a state at the end of the fluid suction. The closed space 9b formed by winding the outer curve 20 and the fixed inner curve 4i indicates a state where compression has been performed from the state shown in Fig. 3 (a), and has the same volume as the closed space 10b. Fig. 3 (c) shows a state in which only a revolving motion is performed at a certain angle from the state of Fig. 3 (b). The closed space 9c formed by spiraling the outer curve 20 and the fixed inner curve 4i and the closed space 1c formed by spiraling the inner curve 2i and the fixed outer curve -11-200521328 (8) have the same volume. When the revolving motion is continuously performed from the state of FIG. 3 (c), the two closed spaces 9 c and 10 c will conduct to the discharge port 7 almost at the same time. Here, in Fig. 3 (b), the closed space 10b formed by winding the inner curve 2i and the fixed outer curve 40 has a Vs' volume independent of the extension of the fixed scroll 4. In addition, the closed space 9b can be regarded as a state at the end of the suction of the fluid formed by the fixed scroll inside curve and the spiral inside curve 2i with the end position a of the fixed outer curve 40 being a, and the volume of the closed space 9b is formed as The same volume Vs' as the confined space 1 Ob. With respect to the volume Vs' of the closed space 9b, the volume Vs of the closed space 9a at the end of the fluid suction formed in the closed space 9a formed by spiraling the outer curve 20 and the fixed inner curve 4i extended to the position b in FIG. 3 (a) is Larger. The volume when the above-mentioned two closed spaces 9a and 9b formed by the spiral outer curve 20 and the fixed inner curve 4i shown in Figs. 3 (a) and 3 (b) are compressed while being conducted to the discharge port 7. , Both are volumes Vd formed in the closed space 9c as shown in FIG. 3 (c). Therefore, by increasing the curling position of the inside curve 4i of the fixed-side scroll body 4 from a to b, the internal volume ratio of the closed space formed by the winding outside curve 20 and the fixed inside curve 4i can be increased. However, the closed space 9a formed in FIG. 3 (a) and the closed space 10a formed in FIG. 3 (b) are both shown in FIG. 3 (c) while being compressed by edges. The internal pressures of the enclosed spaces 9c and 10c are different, so the pressure of the two spaces will cause the internal leakage. Therefore, the liquid jet inlet 8 for cooling the compressor is arranged near the fixed outer curve 40 as shown in Fig. 200521328 (9), and is not connected to the suction 璋 6 and the discharge 璋 7. More compressed fluid can flow into the closed space formed by the spiral inner curve 2i and the fixed outer curve 40, and the pressure in the closed space can be increased. In Figs. 4 (a) to 4 (d), there is shown a state in which the closed space formed by the orbiting scroll body 2 and the fixed scroll body 4 is in communication with the liquid jet inlet 8. Fig. 5 is a graph showing changes in the crank angle with respect to pressure in a closed space formed by a conventional technique having the same outer diameter and a spiral and fixed scroll body of the present invention. Fig. 4 (a) shows a state where the closed space formed by the spiral outer curve 20 and the fixed inner curve 4i of the present invention is just before being conducted to the liquid jet inlet 8, and Fig. 4 (b) shows the above-mentioned airtightness. The space and the liquid jet inlet 8 are formed in an unrelated transient state. Similarly, FIG. 4 (c) shows a state in which the enclosed space formed by the spiral inner curve 2i and the fixed outer curve 40 in this embodiment is just before being conducted to the liquid jet inlet 8 'and FIG. 4 (d ) Indicates a transient state that is not related to the formation of the liquid jet inlet 8. In Figure 5, the vertical axis represents the pressure ratio, the horizontal axis represents the crank angle, and curve 21 represents the closed space formed by the spiral outer curve 20 and the fixed inner curve 4i of the spiral and fixed scroll body of the present invention. The pressure change, curve 22 shows the pressure change around the closed space formed by the inner curve 2i and the fixed outer curve 40, and curve 23 shows the pressure change of the closed space of the conventional technology. In Fig. 5, the compression start points of the curves 2 1 and 2 2 showing the change in the pressure of the machine of the present invention are formed to be different from each other. The reason for 80 degrees is because the inner side is fixed. 13- 200521328 (10) The wall surface is obtained after being extended. effect. Further, the reason why the compression angle of the curve 21 indicating the pressure change in the closed space of the present invention and the curve 23 showing the pressure change in the conventional closed space is different is because the fixed inner wall surface is extended according to the present invention. The effect obtained afterwards and the curl angle of the spiral and fixed scroll are for the sake of increase. The crank angles c and d on the curve 21 correspond to those shown in Figures 4 (a) and 4 (b), and the crank angles e and f on the curve 22 are corresponding to Figure 4 (c) and Figure 4 (d). The pressure in these two closed spaces is increased by the inflow of the compressed fluid flowing from the liquid ejection port at the crank angle from c to d and from e to f. In addition, as shown by the crank angle, the two closed spaces will cause different pressure rises due to the different opening times of the liquid ejection ports. Therefore, for a closed space with a small design pressure and a long opening, the pressure at the crank angle f can be increased The pressure becomes the same as the pressure in the closed space where the design pressure is large. In this way, the pressure of the closed space 10c in FIG. 3 (c) will increase, but the internal pressure of the closed space 9c will not decrease. Therefore, it is possible to alleviate when the discharge port 7 of the two closed spaces 9c and 10c is turned on. The pressure is unbalanced to reduce internal leakage. [Brief description of the drawings] Fig. 1 is a plan view of a scroll portion of a scroll compressor according to an embodiment of the present invention. Fig. 2 is a sectional view of a scroll compressor of the present invention. Fig. 3 is a plan view showing a compression stroke of a scroll compressor of the scroll compressor of the present invention. Fig. 4 is a plan view showing the closed space of the scroll body of the scroll compressor of the present invention and the conduction state of the liquid jet inlet; Fig. 5 is a graph showing the crank angle and pressure of the present invention and the conventional technology. -No. 6 | Stomach A graph showing the crank angle and pressure of the present invention and the conventional technology. [Description of main component symbols] 1: spiral scroll 2 = spiral scroll 3: fixed scroll 4: fixed scroll 5: fixed scroll end plate 6: suction port 7: discharge port | 8: liquid jet flow inlet 18: suction pipe 1 9: spray pipe 20: discharge pipe -15-