1266830 (1) 九、發明說明 【發明所屬之技術領域】 本發明，是關於渦卷式壓縮機。 【先前技術】 渦卷式壓縮機，是具有：將渦捲狀的齒卷片立設於台 板的固定渦卷、及將渦捲狀的齒卷片立設於鏡板的繞轉渦 Φ 卷。渦卷式壓縮機，是使兩渦卷的齒卷片相互嚙合並相面 對配置，藉由使繞轉渦卷繞轉並依序縮小形成於彼此的齒 卷片間的複數壓縮室的容積，來壓縮流體。 藉由此壓縮作用，來發生使固定渦卷及繞轉渦卷相互 分離的軸方向的力（以下稱分離力）。若兩渦卷分離的話 ，會在齒卷片的齒頂及齒底之間產生間隔而使壓縮室的密 閉性悪化，就會降低壓縮機的效率。 在此，在繞轉渦卷的鏡板的裏面，形成成爲吐出壓力 Φ及吸入壓力之間的中間壓力的負壓室，藉由負壓使繞轉渦 卷朝固定渦卷側按壓，來抵消分離力，並且發生讓繞轉渦 卷按壓於固定渦卷的力。 但是，藉由此按壓力而在固定渦卷及繞轉渦卷的鏡板 面中產生滑動摩擦，當按壓力過大的情況時會在鏡板面引 起烙印現象，並減損壓縮機的信賴性。 ’ 爲了降低鏡板面的滑動損失，並提高壓縮機的信賴性 ，在專利文獻1的渦卷式壓縮機中，藉由在鏡板面上呈略 等間距配設由圓弧形狀或是直線形狀等構成的複數油溝， -5- (2) 1266830 就可確實構成將潤滑油供給至滑動部的構造。 〔專利文獻1〕日本特開平7-208 3 5 6號公報 【發明內容】 (本發明所欲解決的課題） 專利文獻1的技術，是將複數油溝略等間距設置於鏡 板面，使鏡板面的潤滑狀態良好。但是，對於鏡板面上的 φ從負壓室朝吸入室或是壓縮室的流體的洩漏就未特別考慮 〇 本發明的課題，是降低由鏡板面上的洩漏所導致的損 失0 (用以解決課題的手段） 爲了解決上述的課題，本發明的渦卷式壓縮機，具備 :立設於台板的渦捲狀之齒卷片；及具有與此齒卷片的先 φ端面連續且設在該齒卷片的周圍的鏡板面的固定渦卷；及 在前述固定渦卷的齒卷片之間具有形成複數壓縮室的渦捲 狀的齒卷片及立設此齒卷片的鏡板之繞轉渦卷；及將前述 繞轉渦卷的鏡板按壓於前述固定渦卷的鏡板面使在前述壓 縮室中具有介於被壓縮的氣體的壓力及被前述壓縮室吸入 的氣體的壓力之間的中間壓力之負壓室；及讓前述負壓室 的壓力導入至相互相面對滑動的前述繞轉渦卷鏡板的鏡板 面及前述固定渦卷的鏡板面的至少任一方的鏡板面之負壓 空間。 -6 - (3) 1266830 藉由上述結構，使作用於繞轉渦卷 加於固定渦卷及繞轉渦卷的鏡板滑動面 片中心成爲基點讓繞轉渦卷鏡板的所期 渦卷的鏡板面，就可以降低鏡板面上的 且上述結構之外，在前述固定渦卷 部附近設有吸入壓領域，且在對於前述 渦捲中心對稱的前述固定渦卷的鏡板面 φ 也可以。 進一步，前述負壓空間的周方向的 述吸入壓領域的周方向的長度等同的長 〇 且，上述結構之外，前述負壓空間 滑動的前述繞轉渦卷鏡板的鏡板面及前 面的至少任一個的相對面的段差部也可 且，在前述固定渦卷的鏡板面的外 φ，前述負壓空間是從該環狀的溝部朝渦 段差部也可以。 進一步，上述結構之外，設在前述 齒卷片端部附近的吸入壓領域的半徑方 定渦卷的鏡板面的半徑方向長度，是比 前述固定渦卷的壓縮室或是吸入室爲止 間滑動的鏡板滑動距離更大也可以。 且，爲了解決上述課題，本發明的 備：立設於台板的渦捲狀之齒卷片；及 的背部的負壓可施 ，就能以渦卷齒卷 的範圍按壓於固定 氣體洩漏。 齒卷片的齒卷片端 固定渦卷齒卷片的 設有前述負壓空間 長度，是至少與前 度或是更長也可以 ，是設在相互面對 述固定渦卷的鏡板 側具備環狀的溝部 捲中心方向擴大的 固定渦卷齒卷片的 向外側中的前述固 從前述負壓空間至 的前述鏡板面彼此 渦卷式壓縮機，具 具有與此齒卷片的 -7- (4) 1266830 先端面連續且設在該齒卷片的周圍的鏡板面的固定渦卷； 及在前述固定渦卷的齒卷片之間具有形成複數壓縮室的渦 捲狀的齒卷片及立設此齒卷片的鏡板之繞轉渦卷；及將前 述繞轉渦卷的鏡板按壓於前述固定渦卷的鏡板面使在前述 壓縮室中具有介於被壓縮的氣體的壓力及被前述壓縮室吸 入的氣體的壓力之間的壓力之負壓室；且，對於分隔該負 壓室及前述壓縮室或是吸入供壓縮用的氣體的吸入室之間 φ 並相互滑動的前述兩渦卷的鏡板滑動面上的密封長度爲最 小的部分，使以前述固定渦卷齒卷片的渦捲中心爲基準與 前述成爲最小的部分對稱側的密封長度，比前述成爲最小 的部分的密封長度更長，而從前述固定渦卷齒卷片的內側 壁面的最外周部至前述繞轉渦卷鏡板的外周部爲止的密封 長度之中，比當與前述繞轉渦卷的繞轉運動時的最小的長 度更短。 上述結構之外，比從固定渦卷內線的最外周部至設在 φ固定渦卷鏡板面的環狀溝爲止的長度之中任一較短的長度 更短也可以。 且上述結構之外，前述成爲最小的部分，是設置於前 述固定渦卷齒卷片的齒卷片端部附近的吸入壓領域的半徑 方向外側的前述兩渦卷的鏡板滑動面也可以。一 (發明之效果） 依據本發明，可以降低固定渦卷繞轉的渦卷的鏡板面 上的從負壓室朝吸入室或是壓縮室的洩漏損失。 -8- (5) 1266830 【實施方式】 以下，參照圖面說明本發明的一實施例。第1圖是顯 不本實施例的渦卷式壓縮機的整體的剖面圖。如第1圖所 不’固定渦卷7，是具有：圓板狀的台板7 a ;及在此台板 7 a上呈渦卷狀立設的齒卷片7 b ;及位置於台板7 a的外周 側，具有與齒卷片7b的先端面連續的鏡板面並包圍齒卷 φ片7b的筒狀的支撐部7d。 立設有齒卷片7b的台板7a的表面，因爲是位於台板 7a及齒卷片7b之間所以也稱作齒底7c。且，支撐部7d 中的與繞轉渦卷8的鏡板8a接觸的面，是固定渦卷7的 鏡板面7e 〇 固定渦卷7，是經由支撐部7d利用螺絲等固定於框架 1 7，與固定渦卷7 —體形成的框架1 7，是藉由熔接等的固 定手段固定於外殼9。 # 另外，繞轉渦卷8，是相面對於固定渦卷7配置，在 框架1 7內繞轉可能。繞轉渦卷8，是具有：圓板狀的鏡板 8a、及與固定渦卷7的齒卷片7b同樣從鏡板8a的表面也 就是齒底8c立設的渦卷狀的齒卷片8b、及設在鏡板8a的 裏面中央的轂部8d。且，鏡板8a的外周部的與固定渦卷 7接觸的表面，是成爲繞轉渦卷8的鏡板面8 e。 外殻9，是將由固定渦卷7及繞轉渦卷8構成的渦卷 部、馬達1 6、潤滑油收納於內部，成爲密閉構造。具備馬 達1 6的旋轉件1 6 a的軸1 〇，是可旋轉自如地設在框架1 7 -9- (6) 1266830 ，成爲與固定渦卷7的軸線同軸。 在軸10的先端設有曲柄l〇a，曲柄10a是安裝在被設 置於繞轉渦卷8的轂部8 d的繞轉軸承1 1，繞轉渦卷8是 可旋轉地安裝於軸1 〇。這時，繞轉渦卷8的軸線是設成對 於固定渦卷7的軸線只偏心預定距離（5狀態。且，繞轉渦 卷8的齒卷片8b，是與固定渦卷7的齒卷片7b在周方向 只錯開預定角度地重疊。 P 而且，安裝有歐丹環12，其是作爲供拘束繞轉渦卷8 無法自轉並對於固定渦卷7可進行相對的繞轉運動用的機 構。 且設置於鏡板面7e的外周部分的環狀溝1 9，是具有 離鏡板面7e不同預定高度的面，使繞轉渦卷8的鏡板面 8 e的端部是隨著繞轉渦卷8的公轉運動通過其上方。這種 環狀溝1 9因爲是面對於負壓空間，所以繞轉渦卷8的鏡 板面8 e的端部’即使是隨著繞轉渦卷8的公轉運動而與 馨環狀溝1 9重疊，也可在負壓空間讓鏡板面8 e成爲開放的 狀態。 在此狀態下讓繞轉渦卷8進行繞轉運動時，在齒卷片 7 b、8 b間，形成有可隨著朝中央部移動使容積連續地縮小 的月牙狀的複數壓縮室1 3。例如，在如第2圖所示的繞轉 渦卷齒卷片8 b的內線側及外線側，分別形成繞轉內線側 壓縮室1 3 a及繞轉外線側壓縮室1 3 b。且，吸入室2 3，是 吸入流體的途中的空間。此吸入室2 3，是從當繞轉渦卷8 的繞轉運動的位相前進並成爲封閉流體完成時點開始成爲 -10- (7) 1266830 壓縮室13。 吸入口 1 4，是設置於固定渦卷7。此吸入口 1 4是 設台板7 a的外周側而與吸入室2 3連通。從吸入口 1 4 入的流體，在藉由吸入室23封閉且直到重新與吸入室 連通爲止，成爲吸入壓力。此流體成爲吸入壓的領域就 吸入壓領域。大致上，此吸入壓領域是位置於固定渦卷 卷片7b的齒卷片端部分附近。因此，此吸入壓領域附 φ 的固定渦卷鏡板面7e是半徑方向的長度短且密封距離 易充分取得的部分。且，吐出口 1 5，是穿設固定渦卷7 台板7a的渦捲中心附近而與最內周側的壓縮室1 3連通 接著說明其作動。首先，藉由馬達1 6驅動旋轉軸 的話，此旋轉是從軸1 〇的曲柄1 〇a通過繞轉軸承1 1傳 至繞轉渦卷8。由此，繞轉渦卷8是以固定渦卷7的軸 爲中心並以具有預定距離6的繞轉半徑進行繞轉運動。 繞轉運動時的繞轉渦卷8是無法自轉地被歐丹環1 2拘 • 〇 而且，藉由繞轉渦卷8的繞轉運動，各齒卷片7b、 之間所形成的壓縮室1 3會在中央連續移動，隨著該移 使壓縮室13的容積連續地縮小。藉此，將從吸入口 14 入的流體在各壓縮室1 3內依序壓縮後，讓被壓縮的流 從吐出口 1 5吐出。被吐出的流體，是通過外殻9內從 出配管6，供給至例如冷凍循環管線中。 另外，潤滑油是被貯留於外殻9的底部，而使周圍 壓力成爲吐出壓力。由框架17、軸1 〇、固定渦卷7、繞 穿 流 23 是 齒 近 不 的 〇 10 達 線 此 束 8b 動 吸 體 吐 的 轉 -11 - (8) 1266830 渦卷8所形成的負壓室1 8內的壓力因爲比吐出壓更低， 所以貯留於外殼9的底的潤滑油是通過被設在軸1 〇中的 貫通孔3流入負壓室1 8。具體上，潤滑油的一部分是通過 軸1 0中的橫孔4同時潤滑主軸承5後到達負壓室1 8。 且，其他的潤滑油，是通過貫通孔3到達軸1 0的曲 柄1 0a上部，潤滑繞轉軸承1 1後進入負壓室1 8。在此， 潤滑油，是在通過主軸承5及繞轉軸承1 1時，因爲軸承 φ間隙小而被縮徑節流且以比吐出壓力更低的壓力進入負壓 室1 8。已進入負壓室1 8的潤滑油，當負壓變高的話，被 設在朝吸入室23的連通路中的負壓調整閥2會被打開而 進入吸入室23。而且，通過壓縮室13從吐出口 15吐出的 潤滑油，其一部分是從吐出配管6朝冷凍循環管線吐出， 剩下是與冷媒分離地被貯留於外殼9內的底部。 接著，說明兩渦卷的鏡板面上的流體的洩漏。在渦卷 式壓縮機中，藉由該壓縮作用，會發生使固定渦卷7及繞 Φ轉渦卷8相互分離的軸方向的力。兩渦卷分離的話，壓縮 室的密閉性會悪化而降低壓縮機的效率。 在此，在繞轉渦卷8的鏡板的裏面側，設有成爲吐出 壓力及吸入壓力之間的中間壓力的負壓的負壓室1 8，藉由 該負壓抵消分離力，並且將繞轉渦卷8按壓於固定渦卷7 。這時，繞轉渦卷8的鏡板面8 e及固定渦卷7的鏡板面 7e會相互滑動。 此鏡板上的滑動面，是隔有微小間隙相面對，如第4 圖所不，具有分隔負壓室18及吸入室23或是壓縮室13 -12- (9) 1266830 的功能。此滑動面的間隙的大小，是隨著鏡板面上的位置 及時間而變化。其理由如下述。 在運轉時的繞轉渦卷8中，藉由壓縮作用，不只有產 生軸方向的力也產生接線方向及半徑方向的力’且也產生 離心力。藉由這些的力可發生讓繞轉渦卷8傾斜的翻覆力 矩。因此繞轉渦卷8進行擺動運動時，兩鏡板面就無法隨 時保持平行，間隙的大小也不固定。此間隙愈小’鏡板面 φ 上的洩漏就愈小。 且，在鏡板面上的拽漏，也會影響第2圖及第4圖所 示的密封長度。密封長度，是固定渦卷7及繞轉渦卷8的 鏡板滑動面的半徑方向的長度，且是分隔負壓室1 8及壓 縮室13或是吸入室23的長度。 例如，在吸入口 1 4附近的密封長度，是第2圖（A ) 中的點24及點25間的長度，在第2圖（C)中的點24及 點26間的長度。在此，點24是固定渦卷內線的最外周上 φ的點，點25是設在固定渦卷鏡板面7e的環狀溝1 9的內 周上的點，點2 6是繞轉渦卷鏡板外周上的點。 藉由繞轉渦卷的繞轉運動的位相來變化密封長度，各 位相的密封長度，是成爲點24及點25間的長度或是點24 及點26間的長度的任一較短的長度。順便一提，若無環 狀溝1 9的情況時，就成爲點24及點26間的長度，繞轉1 圈中只會增減半徑的2倍的長度。之後的密封長度，爲了 方便，是顯示繞轉1圈中的密封長度的最小値。 密封長度愈短密閉性愈悪化就會使洩漏損失增大。密 -13- (10) 1266830 封長度是依據鏡板面上的位置而有不同，在習知的渦卷式 壓縮機中，在吸入口 1 4附近的密封長度因爲最短，所以 在吸入口 1 4附近的鏡板面的洩漏損失，就會比鏡板面上 的其他部分大。 進一步，在吸入口 14附近，密封前後的壓力差，是 成爲負壓及吸入壓力的差，相比於成爲負壓及壓縮室內壓 力的差的鏡板面上的其他的部分，洩漏會更大。本發明， 馨是在此洩漏較大的吸入口 1 4附近，加強讓繞轉渦卷8按 壓固定渦卷7的力，縮小鏡板面間的間隙，來降低洩漏。 對於本實施例的結構，進一步詳細說明。如第3圖所 示，在固定渦卷7的鏡板面7e設有溝1。溝1，是開設在 環狀溝f 1 9且成爲與負壓，室：1 8幾乎無縮徑地讓流體連通的 空間。此溝1，是對於密封長度最短的吸入口 14附近，以 渦捲中心20爲基準通過成爲略點對稱的位置。而且周方 向的長度，若以點對稱將溝1平移至相反側的話，具備可 馨覆蓋吸入口 1 4附近例如至少吸入壓領域的長度。 圖示的固定渦卷7，是從外側依序並列：安裝有供固 定於框架1 7用的螺絲等的結合具的支撐部7d、環狀溝1 9 、鏡板面7e、將鏡板面76的內惻側壁作爲一部分對於渦 捲中心20呈渦卷狀捲撓的齒卷片7b。溝1，若改變視角 的話，是形成使環狀溝1 9的一部分對於鏡板面7e變廣的 形狀，或是朝中心20的方向使環狀溝的溝寬變廣。且溝1 ，是設置於固定渦卷7的鏡板面7e的段差。即使不具有 例如環狀溝19，也可藉由被設置於鏡板面7e的段差也就 -14- (11) 1266830 是溝1導入負壓。 接著，說明本實施例的特徵結構的作用。第4圖，是 意示繞轉渦卷8的鏡板面8e所產生的壓力分布。第4圖 是當設有溝1的情況時的壓力分布，第5圖是未設置溝i 的情況時的壓力分布。 設有溝1的情況時，溝1內的壓力因爲成爲負壓，所 以與未設置溝1的情況相比，只有由三角形顯示的領域2 2 φ 的部分，增加從上方按壓繞轉渦卷8的鏡板面8 e的力。 即，繞轉渦卷8的鏡·板面8 e的將對應溝1的領域從上朝 下按壓的方向的力矩，是加上了翻覆力矩後重新產生。 這時，繞轉渦卷鏡板面8 e的以渦捲中心2 0爲基準與 對應清I的位置成爲略點對稱的逆側的領域，會按壓於固 定渦卷7的鏡板面7e。該被按壓的部分，是藉由調整溝1 的位置使鏡板面的密封長度成爲最短的部分，就可增大密 封長度爲短的部分的按壓力，並可降低洩漏損失。 # 又，溝1及環狀環狀溝1 9的連接部分2 1，是藉由以 圓弧形成等的方法，儘可能不尖銳而平滑地精整完成較佳 。這是因爲，設在鏡板面的溝的端部有尖銳部分的話，當 擺動運動而使繞轉渦卷8傾斜時會有接觸的可能性，而有 可能損塲鏡板面。 在上述實施例中，雖說明將溝1設置於固定渦卷7的 鏡板面7e的例，但是溝1是如第6圖所示的形狀也可以 。即’如第6圖所示的溝1，是如文字所述從負壓空間插 入的溝’使內部成爲與負壓等同壓力的空間。在此對於該 -15- (12) 1266830 溝1的空間，對於以渦捲中心2 0爲基準相反側的與吸入 口 14連通的吸入壓力空間附近的齒卷片7b及鏡板面7e 特別是接近於負壓空間也就是環狀溝1 9的鏡板面7e，可 達成按壓繞轉渦卷8的鏡板面8e的作用。 且，如第7圖及其剖面圖也就是第8圖所示，即使將 溝1設置繞轉渦卷8的鏡板面8e也可實現同等的功能。 此情況，在構造上是對於繞轉渦卷8的鏡板面.8e的段差 φ 部。對於鏡板面7e即使是從環狀溝延伸的溝1，但對於鏡 板面7e也是段差部，而爲負壓導入空間。 【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 面圖。 〔第2圖〕由第1圖的繞轉渦卷及固定渦卷構成的壓 縮室的平面圖。1266830 (1) Description of the Invention [Technical Field of the Invention] The present invention relates to a scroll compressor. [Prior Art] A scroll compressor has a fixed scroll in which a spiral-shaped toothed piece is erected on a platen, and a winding vortex Φ in which a spiral-shaped toothed piece is erected on the mirror plate. . The scroll compressor is such that the two scroll wraps are meshed with each other and face each other, and the volume of the plurality of compression chambers formed between the mutually wound flakes is sequentially rotated by the wraparound vortex To compress the fluid. By this compression action, a force in the axial direction (hereinafter referred to as a separation force) that separates the fixed scroll and the orbiting wrap is generated. If the two scrolls are separated, a gap is formed between the crests and the bottom of the toothed piece to decompose the tightness of the compression chamber, which reduces the efficiency of the compressor. Here, in the inside of the mirror plate around the wrap, a negative pressure chamber which is an intermediate pressure between the discharge pressure Φ and the suction pressure is formed, and the wraparound scroll is pressed toward the fixed wrap side by the negative pressure to cancel the separation. Force, and the force that causes the orbiting scroll to press against the fixed scroll. However, by this pressure, sliding friction is generated in the mirror surface of the fixed scroll and the orbiting scroll, and when the pressing force is excessive, the stamping phenomenon is caused on the mirror surface, and the reliability of the compressor is degraded. In order to reduce the sliding loss of the mirror plate surface and improve the reliability of the compressor, in the scroll compressor of Patent Document 1, the arc shape or the straight shape is arranged at a slightly equal interval on the mirror plate surface. The plurality of oil grooves formed, -5- (2) 1266830, can surely constitute a structure for supplying lubricating oil to the sliding portion. [Patent Document 1] Japanese Laid-Open Patent Publication No. Hei 7-208 No. 3-6 (Concerned) (Problems to be Solved by the Invention) The technique of Patent Document 1 is to provide a plurality of oil grooves at equal intervals on a mirror plate surface to form a mirror plate. The lubrication of the surface is good. However, the leakage of the fluid from the negative pressure chamber to the suction chamber or the compression chamber on the mirror surface is not particularly considered in the present invention, and the loss caused by the leakage on the mirror surface is reduced. In order to solve the above problems, the scroll compressor of the present invention includes: a spirally wound toothed piece that is erected on a platen; and has a continuous φ end face of the toothed piece and is provided a fixed scroll of the mirror plate surface around the toothed piece; and a spiral-shaped toothed piece forming a plurality of compression chambers between the toothed sheets of the fixed scroll and a mirror plate around which the toothed piece is erected And rotating the mirror plate of the orbiting wrap to the mirror plate surface of the fixed scroll so as to have a pressure between the compressed gas and the pressure of the gas sucked by the compression chamber in the compression chamber a negative pressure chamber of the intermediate pressure; and a negative pressure of the mirror plate surface of the mirror plate surface of the rotating scroll mirror plate and the mirror plate surface of the fixed scroll which are brought into contact with each other by the pressure of the negative pressure chamber space. -6 - (3) 1266830 With the above structure, the center of the sliding plate of the mirror plate which is applied to the fixed scroll and the orbiting wrap is used as a base plate for rotating the scroll plate of the scroll plate. Further, in addition to the above configuration, the surface of the mirror plate may be lowered, and a suction pressure region may be provided in the vicinity of the fixed scroll portion, and the mirror plate surface φ of the fixed scroll that is symmetrical with respect to the center of the scroll may be provided. Further, the length of the suction pressure field in the circumferential direction of the negative pressure space is equal to the length of the circumferential direction, and in addition to the above configuration, at least the mirror surface of the orbiting scroll plate that slides in the negative pressure space and the front surface are at least The step portion of the opposing surface may be the outer diameter φ of the mirror plate surface of the fixed scroll, and the negative pressure space may be from the annular groove portion to the vortex step portion. Further, in addition to the above configuration, the radial length of the mirror plate surface of the radius constant scroll provided in the vicinity of the end portion of the toothed piece is slidable between the compression chamber or the suction chamber of the fixed scroll. The sliding distance of the mirror plate is also larger. Further, in order to solve the above problems, the present invention provides a scroll-shaped toothed piece that is erected on a platen; and a negative pressure on the back can be applied to press the fixed gas to leak in the range of the spiral wrap. The length of the negative pressure space of the toothed piece end of the toothed piece is set to be at least the front or the length, and is provided on the side of the mirror plate facing the fixed scroll. In the outer side of the fixed scroll portion in which the center of the fixed scroll is enlarged, the aforementioned mirror plate surface is spirally compressed from the negative pressure space, and has a -7- (4) with the toothed piece. 1266830 a fixed scroll having a face end continuous and disposed on a mirror plate surface around the toothed piece; and a scroll-shaped toothed piece and a standing body forming a plurality of compression chambers between the fixed scrolls of the fixed scroll a rotating scroll of the mirror plate of the toothed piece; and pressing the mirror plate of the rotating wrap to the mirror plate surface of the fixed scroll to have a pressure between the compressed gas in the compression chamber and being compressed by the compression chamber a negative pressure chamber for the pressure between the pressures of the inhaled gas; and a mirror plate of the two scrolls that φ and slides between the negative pressure chamber and the compression chamber or the suction chamber for sucking the gas for compression The length of the seal on the sliding surface is In the small portion, the seal length on the symmetrical side of the portion which is the smallest portion based on the center of the wrap of the fixed scroll wrap is longer than the seal length of the smallest portion, and the fixed wrap is from the aforementioned The seal length of the outermost peripheral portion of the inner wall surface of the winding sheet to the outer peripheral portion of the orbiting scroll plate is shorter than the minimum length when the wrap motion of the orbiting wrap is performed. In addition to the above configuration, the shorter one of the lengths from the outermost peripheral portion of the fixed scroll inner line to the annular groove provided on the φ fixed scroll mirror surface may be shorter. In addition to the above-described configuration, the smallest portion may be the mirror sliding surface of the two scrolls provided on the outer side in the radial direction of the suction pressure region in the vicinity of the end portion of the convolute piece of the fixed scroll wrap. (Effect of the Invention) According to the present invention, it is possible to reduce the leakage loss from the negative pressure chamber to the suction chamber or the compression chamber on the mirror surface of the scroll of the fixed scroll winding. -8- (5) 1266830 [Embodiment] Hereinafter, an embodiment of the present invention will be described with reference to the drawings. Fig. 1 is a cross-sectional view showing the entirety of a scroll compressor of the present embodiment. As shown in Fig. 1, the fixed scroll 7 has a disk-shaped platen 7a; and a sprocket 7b which is erected on the platen 7a; and is positioned on the platen The outer peripheral side of 7 a has a cylindrical support portion 7d which is continuous with the front end surface of the sprocket piece 7b and surrounds the φ piece 7b. The surface of the platen 7a on which the sprocket piece 7b is provided is also referred to as the tooth bottom 7c because it is located between the platen 7a and the sprocket piece 7b. Further, the surface of the support portion 7d that is in contact with the mirror plate 8a of the orbiting scroll 8 is the mirror plate surface 7e of the fixed scroll 7, and the fixed scroll 7 is fixed to the frame 17 by screws or the like via the support portion 7d. The frame 17 formed of the fixed scroll 7 is fixed to the outer casing 9 by fixing means such as welding. # In addition, the orbiting wrap 8 is a face-to-face arrangement for the fixed wrap 7 and may be rotated within the frame 17. The orbiting wrap 8 is a disk-shaped mirror plate 8a having a disk shape, and a spiral-shaped toothed piece 8b which is erected from the surface of the mirror plate 8a, that is, the tooth bottom 8c, similarly to the toothed piece 7b of the fixed scroll 7. And a hub portion 8d provided at the center of the inner surface of the mirror plate 8a. Further, the surface of the outer peripheral portion of the mirror plate 8a that is in contact with the fixed scroll 7 is the mirror plate surface 8e that surrounds the wrap 8. The outer casing 9 has a scroll portion composed of the fixed scroll 7 and the orbiting scroll 8, a motor 16 and a lubricating oil housed therein, and has a sealed structure. The shaft 1 具备 having the rotating member 16 a of the motor 16 is rotatably provided to the frame 1 7 -9-(6) 1266830 so as to be coaxial with the axis of the fixed scroll 7. A crank la is provided at the tip end of the shaft 10, and the crank 10a is mounted on a wraparound bearing 1 1 provided on the hub portion 8d of the wrap wrap 8, and the wrap wrap 8 is rotatably mounted to the shaft 1 Hey. At this time, the axis of the orbiting scroll 8 is set to be eccentric only a predetermined distance (5 state) with respect to the axis of the fixed scroll 7, and the sprocket 8b of the orbiting wrap 8 is a sprocket with the fixed wrap 7. 7b is overlapped by a predetermined angle in the circumferential direction. P Further, the Audan ring 12 is attached as a mechanism for the rotation of the wrap-around wrap 8 so that it can not rotate and the relative wrap 7 can be rotated relative to the fixed wrap 7. The annular groove 196 at the outer peripheral portion of the mirror plate surface 7e is a surface having a predetermined height different from the mirror plate surface 7e, so that the end portion of the mirror plate surface 8e of the orbiting wrap 8 is revolved with the orbiting wrap 8. The movement passes over it. Since the annular groove 1 9 faces the negative pressure space, the end portion of the mirror plate surface 8 e of the orbiting scroll 8 is even with the revolving motion of the orbiting scroll 8 The annular groove 19 is overlapped, and the mirror plate surface 8 e can be opened in the negative pressure space. When the orbiting wrap 8 is rotated in this state, between the toothed sheets 7 b and 8 b, A crescent-shaped plural compression chamber 13 that can continuously reduce the volume as it moves toward the central portion is formed. For example, As shown in Fig. 2, the inner-line side and the outer-line side of the orbiting scroll 8b are formed around the inner-side compression chamber 13a and the outer-side compression chamber 13b, respectively. 3. A space in the middle of inhalation of the fluid. The suction chamber 23 starts to become a 10- (7) 1266830 compression chamber 13 from the point when the revolving motion of the orbiting wrap 8 advances and becomes a closed fluid. The suction port 14 is provided in the fixed scroll 7. The suction port 14 is provided on the outer peripheral side of the platen 7a and communicates with the suction chamber 23. The fluid from the suction port 14 is in the suction chamber 23 The suction pressure is closed until it is reconnected to the suction chamber. The fluid is in the suction pressure field in the field of suction pressure. Generally, the suction pressure field is located near the end portion of the fixed scroll sheet 7b. The fixed scroll mirror surface 7e with φ in the suction pressure field is a portion in which the length in the radial direction is short and the sealing distance is easily obtained. Further, the discharge port 15 is a scroll center through which the fixed scroll 7 plate 7a is inserted. In the vicinity, it communicates with the compression chamber 13 on the innermost circumference side, and then explains First, when the rotating shaft is driven by the motor 16, the rotation is transmitted from the crank 1 〇a of the shaft 1 通过 through the orbiting bearing 1 1 to the orbiting scroll 8. Thus, the orbiting scroll 8 is The axis of the fixed scroll 7 is centered and revolves with a revolving radius having a predetermined distance 6. The orbiting wrap 8 during the revolving motion is incapable of being rotated by the Ou Dan ring 1 2 and by revolving The revolving motion of the wrap 8 causes the compression chambers 13 formed between the respective flakes 7b to continuously move in the center, and the volume of the compression chamber 13 is continuously reduced as the movement is made. After the fluid that has entered 14 is sequentially compressed in each compression chamber 13, the compressed flow is discharged from the discharge port 15. The fluid to be discharged is supplied from the outlet pipe 6 through the inside of the casing 9 to, for example, a refrigeration cycle line. Further, the lubricating oil is stored at the bottom of the outer casing 9, and the surrounding pressure becomes the discharge pressure. From the frame 17, the shaft 1 〇, the fixed scroll 7, and the through-flow 23 are the teeth 10 which are close to the line. The bundle 8b is sucked by the moving body -11 - (8) 1266830 The negative pressure formed by the scroll 8 Since the pressure in the chamber 18 is lower than the discharge pressure, the lubricating oil stored in the bottom of the casing 9 flows into the negative pressure chamber 18 through the through hole 3 provided in the shaft 1 . Specifically, a part of the lubricating oil is simultaneously lubricated by the transverse hole 4 in the shaft 10 to the negative pressure chamber 18 after being simultaneously lubricated. Further, the other lubricating oil passes through the through hole 3 to reach the upper portion of the crank 10a of the shaft 10, and the lubricating bearing 1 1 is lubricated and then enters the negative pressure chamber 18. Here, when the lubricating oil passes through the main bearing 5 and the revolving bearing 1 1 , the bearing φ has a small gap and is reduced in diameter and throttled, and enters the negative pressure chamber 18 at a pressure lower than the discharge pressure. The lubricating oil that has entered the negative pressure chamber 18 is opened, and when the negative pressure becomes high, the negative pressure regulating valve 2 provided in the communication passage toward the suction chamber 23 is opened to enter the suction chamber 23. Further, a part of the lubricating oil discharged from the discharge port 15 through the compression chamber 13 is discharged from the discharge pipe 6 to the refrigeration cycle line, and the remaining portion is stored in the bottom portion of the casing 9 separately from the refrigerant. Next, the leakage of the fluid on the mirror surface of the two scrolls will be described. In the scroll compressor, the axial direction force which causes the fixed scroll 7 and the Φ rotating scroll 8 to be separated from each other occurs by the compression. When the two scrolls are separated, the tightness of the compression chamber is degraded and the efficiency of the compressor is lowered. Here, on the back side of the mirror plate around the wrap 8 , a negative pressure chamber 1 8 which is a negative pressure which is an intermediate pressure between the discharge pressure and the suction pressure is provided, and the separation force is canceled by the negative pressure, and the winding force is wound. The wrap 8 is pressed against the fixed scroll 7. At this time, the mirror plate surface 8 e of the orbiting scroll 8 and the mirror plate surface 7e of the fixed scroll 7 slide each other. The sliding surface of the mirror plate is faced with a small gap, as shown in Fig. 4, and has the function of separating the negative pressure chamber 18 and the suction chamber 23 or the compression chamber 13 -12- (9) 1266830. The size of the gap of the sliding surface varies with the position and time on the mirror surface. The reason is as follows. In the orbiting scroll 8 during operation, by the action of compression, not only the force in the axial direction but also the force in the wiring direction and the radial direction is generated and centrifugal force is generated. With these forces, a flipping force that causes the orbiting wrap 8 to tilt can occur. Therefore, when the whirling motion is performed around the wrap 8, the mirror faces of the two mirror plates cannot be kept parallel at the same time, and the size of the gap is not fixed. The smaller the gap, the smaller the leakage on the mirror surface φ. Moreover, the leakage on the mirror surface also affects the seal length shown in Figures 2 and 4. The seal length is the length in the radial direction of the fixed scroll 7 and the mirror sliding surface of the orbiting scroll 8, and is the length separating the negative pressure chamber 18 and the compression chamber 13 or the suction chamber 23. For example, the seal length in the vicinity of the suction port 14 is the length between the point 24 and the point 25 in Fig. 2(A), and the length between the point 24 and the point 26 in Fig. 2(C). Here, the point 24 is a point on the outermost circumference of the fixed scroll inner line φ, the point 25 is a point provided on the inner circumference of the annular groove 19 of the fixed scroll mirror surface 7e, and the point 26 is a winding wrap. The point on the outer perimeter of the mirror plate. The length of the seal is varied by the phase of the orbiting motion of the wrap, and the length of the seal of each phase is either the length between points 24 and 25 or any shorter length between points 24 and 26. . Incidentally, if there is no loop groove 19, the length between the point 24 and the point 26 is obtained, and only about twice the length of the radius is increased or decreased in one revolution. The subsequent seal length, for convenience, is the minimum flaw showing the length of the seal in one revolution. The shorter the seal length, the more the airtightness becomes, and the leakage loss is increased. The density of the seal is different depending on the position on the mirror plate surface. In the conventional scroll compressor, the seal length near the suction port 14 is the shortest, so the suction port 14 The leakage loss of the nearby mirror surface is greater than the rest of the mirror surface. Further, in the vicinity of the suction port 14, the pressure difference between the front and the rear of the seal is the difference between the negative pressure and the suction pressure, and the leakage is larger than the other portions on the mirror surface which are the difference between the negative pressure and the pressure in the compression chamber. In the present invention, in the vicinity of the suction port 14 where the leakage is large, the force for fixing the wrap 7 by the wraparound scroll 8 is strengthened, and the gap between the mirror plates is narrowed to reduce leakage. The structure of this embodiment will be described in further detail. As shown in Fig. 3, a groove 1 is provided in the mirror plate surface 7e of the fixed scroll 7. The groove 1 is a space which is opened in the annular groove f 1 9 and which is in fluid communication with the negative pressure, and the chamber: 18 has almost no diameter reduction. This groove 1 is a position that is slightly symmetrical with respect to the scroll center 20 with respect to the vicinity of the suction port 14 having the shortest seal length. Further, if the length of the circumferential direction is shifted to the opposite side by the point symmetry, it is possible to cover the length of the suction port 14 in the vicinity of, for example, at least the suction pressure field. The fixed scroll 7 shown in the figure is arranged in parallel from the outside: a support portion 7d to which a coupling for fixing to the frame 17 or the like is attached, an annular groove 19, a mirror plate surface 7e, and a mirror plate surface 76 are attached. The inner side wall as a part of the scroll center 20 is spirally wound by the winding piece 7b. When the viewing angle is changed, the groove 1 is formed such that a part of the annular groove 19 is widened toward the mirror plate surface 7e, or the groove width of the annular groove is widened toward the center 20. Further, the groove 1 is a step difference provided on the mirror plate surface 7e of the fixed scroll 7. Even if there is no, for example, the annular groove 19, the step of being provided on the mirror plate surface 7e is also -14-(11) 1266830, and the groove 1 is introduced with a negative pressure. Next, the action of the characteristic structure of the present embodiment will be described. Fig. 4 is a view showing the pressure distribution generated by the mirror plate surface 8e of the orbiting scroll 8. Fig. 4 is a pressure distribution when the groove 1 is provided, and Fig. 5 is a pressure distribution when the groove i is not provided. When the groove 1 is provided, since the pressure in the groove 1 becomes a negative pressure, the portion of the field 2 2 φ which is displayed by the triangle is increased, and the winding wrap 8 is pressed from above as compared with the case where the groove 1 is not provided. The force of the mirror surface 8 e. In other words, the moment of the mirror plate surface 8 e of the orbiting scroll 8 that presses the field corresponding to the groove 1 from the top to the bottom is regenerated after the overturning moment is added. At this time, the field of the spiral wrap plate surface 8e that is slightly symmetrical with respect to the position of the corresponding clear I based on the wrap center 20 is pressed against the mirror plate surface 7e of the fixed wrap 7. In the pressed portion, by adjusting the position of the groove 1 so that the sealing length of the mirror plate surface becomes the shortest portion, the pressing force of the portion having a short sealing length can be increased, and the leakage loss can be reduced. # Further, the connecting portion 2 1 of the groove 1 and the annular annular groove 1 9 is preferably formed by a circular arc or the like, and is preferably finished as sharply and smoothly as possible. This is because if the end portion of the groove provided on the mirror plate surface has a sharp portion, there is a possibility of contact when the whirling wrap 8 is tilted by the swinging motion, and the mirror plate surface may be damaged. In the above embodiment, the example in which the groove 1 is provided on the mirror plate surface 7e of the fixed scroll 7 is described, but the groove 1 may have a shape as shown in Fig. 6. That is, the groove 1 as shown in Fig. 6 is a groove which is inserted from the negative pressure space as described in the figure, and the inside becomes a space equivalent to the negative pressure. Here, the space of the -15-(12) 1266830 groove 1 is particularly close to the sprocket piece 7b and the mirror plate surface 7e in the vicinity of the suction pressure space communicating with the suction port 14 on the opposite side of the scroll center 20 as a reference. In the negative pressure space, that is, the mirror plate surface 7e of the annular groove 19, the action of pressing the mirror plate surface 8e of the orbiting scroll 8 can be achieved. Further, as shown in Fig. 7 and its cross-sectional view, which is shown in Fig. 8, even if the groove 1 is disposed around the mirror plate surface 8e of the orbiting scroll 8, the same function can be realized. In this case, it is structurally the step φ portion of the mirror plate surface .8e of the orbiting scroll 8. The mirror plate surface 7e is a groove 1 extending from the annular groove, but is also a stepped portion for the mirror surface 7e, and is a negative pressure introduction space. BRIEF DESCRIPTION OF THE DRAWINGS [Fig. 1] A longitudinal sectional view of a scroll compressor according to an embodiment of the present invention. [Fig. 2] A plan view of a compression chamber composed of a wraparound scroll and a fixed wrap of Fig. 1.
〔第3圖〕第1圖的固定渦卷的平面圖。 〔第4圖〕意示鏡板面中的壓力分布的圖。 〔第5圖〕意示鏡板面中的壓力分布的圖。 〔第6圖〕本發明的其他的實施例的固定渦卷的平面[Fig. 3] A plan view of the fixed scroll of Fig. 1. [Fig. 4] is a view showing the pressure distribution in the mirror surface. [Fig. 5] is a view showing the pressure distribution in the mirror surface. [Fig. 6] Plane of a fixed scroll of another embodiment of the present invention
〔第7圖〕本發明的進一步其他的實施例的繞轉渦卷 的平面圖。 〔第8圖〕第7圖的A-A剖面圖。 -16- (13) 1266830 【主要元件符號說明】 1 :溝 2 :負壓調整閥 3 :貫通孔 4 :橫孔 5 :主軸承 6 :吐出配管 7 :固定渦卷 7 a :台板 7b :齒卷片 7 c :齒底 7 d :支撐部 7 e :鏡板面 8 :繞轉渦卷 8 a :鏡板[Fig. 7] A plan view of a orbiting scroll of still another embodiment of the present invention. [Fig. 8] A-A cross-sectional view of Fig. 7. -16- (13) 1266830 [Description of main component symbols] 1 : Groove 2 : Negative pressure regulating valve 3 : Through hole 4 : Horizontal hole 5 : Main bearing 6 : Discharge pipe 7 : Fixed wrap 7 a : Platen 7b : Toothed piece 7 c : tooth bottom 7 d : support portion 7 e : mirror plate surface 8 : winding wrap 8 a : mirror plate
8b :齒卷片 8 c :齒底 8 d :轂部 8 e :鏡板面 9 :外殼 10 :軸 1 0 a :曲柄 1 1 :繞轉軸承 1 2 :歐丹環 -17 (14) 1266830 13 :壓縮室8b: Toothed piece 8 c: Tooth bottom 8 d : Hub 8 e : Mirror plate surface 9 : Housing 10 : Axis 1 0 a : Crank 1 1 : Wound bearing 1 2 : Ou Dan ring -17 (14) 1266830 13 : Compression room
1 3 a :繞轉內線側壓縮室 13b :繞轉外線側壓縮室 1 4 :吸入口 15 :吐出口 1 6 :馬達 1 6 a :旋轉件 1 7 :框架 18 :負壓室 1 9 :環狀溝 2 0 .渦捲中 >匕、 21 :連接部分 2 2 :領域 2 3 :吸入室 24 :點 25 :點 26 :點 -181 3 a : revolving inner-side compression chamber 13b: revolving outer-side compression chamber 1 4 : suction port 15 : discharge port 16 6 : motor 1 6 a : rotating member 17: frame 18: negative pressure chamber 1 9 : ring Groove 2 0 . In the wrap > 匕, 21: connecting portion 2 2 : field 2 3 : suction chamber 24: point 25: point 26: point -18