406165 A7 •"-邻中"巧^^9 7,消资":^^印,,;" B7五、發明説明（1 ) 〔發明所屬的技術領域〕 本發明係關於被使用於冷凍循環裝置中的螺旋葉片式 壓縮機之流體機械· 〔先行技術〕 屬於流體機械範轉而構成冷凍循環之壓縮機，過去多 爲採用往復方式、旋轉方式等的各種壓縮機，但將回轉力 傳達至壓縮機構部之驅動部或壓縮部的構造較爲複雜•且 增加零件數量· 另外*爲了提高壓縮效率而在吐出側設置止回閥（ checkvalve)，但是，由於止回閥兩側的Μ力差非常的大 *所以氣體容易從止回閥洩漏。爲了解決這種問題，必須 提髙各零件的尺寸精度或裝配精度，結果造成製造成本增 加β 因此，近年來，已被提案有被稱爲流體壓縮機的螺旋 葉片式壓縮機。此壓縮機，其作爲被連結至回轉驅動源的 回轉體之滾筒，被偏心地配置在汽缸內•且與汽缸同步地 被回轉驅動•在此滾筒的周面上，設有螺旋狀溝，且旋繞 著出入自由的葉片· 在上述葉片與浪筒周面及汽缸內周面之間，形成作爲 作動室的壓縮室，將作爲作動流體的冷媒氣體吸入上述壓 縮室的一端部內，一邊逐漸地移送至他端部一邊壓縮· 因此·可以除去以往壓縮機的缺點，以較簡單的構成 來提昇密閉性而能達成效率良好的壓縮*同時零件的製造 (誚先閱讀背而之注意事項再填巧本頁) •1Τ 線 本纸張尺度这;1〗中SS家標泠（（'NS ) Λ4現格（210X297公釐） __406165 b7__ 五、發明説明（2 ) 及裝配變容易· 〔發明所欲解決的課題〕 __ 不過，此種壓縮機*係以螺旋形狀來決定壓縮比，而 當低回轉時或起動時，將處於偏離設計壓縮比的領域，而 在壓縮比低的運轉狀態下將產生過壓縮，導致顯著降低壓 縮性能· 另外，例如在空調負荷較小時會有液壓縮現象•壓縮 室超過規定壓力而變成異常高壓，特別是對作爲合成樹脂 系製的彈性構件之葉片加諸應力，易於導致破損。 壓縮室的異常髙壓狀態在一定的條件下確定會產生， 而無法避免•必須具備即使形成此狀態也能阻止葉片的破 損之手段；本專利申請人先前已提案了在日本專利特開平 5 — 7 1 4 8 2號公報所掲示的流體壓縮機· 此技術，其特徵爲：在區隔壓縮室之葉片，設置當壓 縮過程中的壓力超過規定壓力時，將其壓力放出至吐出側 的作動室之放出通路，減低加諸在上述葉片的應力· 不過，若僅設置放出通路，將導致葉片的肉厚被減少 ，於是會發生扭曲變形而易於折損葉片，導致信賴性降低 〇 又，作爲葉片的成形手段，係先將葉片成形爲規定的 形狀後，以切削加工來形成上述放出通路，所以不易製造 本發明係鑑於上述情況而開發出來，其目的爲提供一 本纸ίί、尺度询中囚囚家標彳（CNS > Λ4規格（210X297公釐) I- - - - - - 1Γ·. (¾先閱讀背而之注意事項再堉巧本頁) .I n^i HI 111 I 士> _ 1 n mf ml i - V nn ml 1^1 線 -5 - 406165 A7 _ _' B7 ____五、發明说明（3 ) 種螺旋葉片式流體機械，不論是在任何原因下作動室形成 異常髙壓時，能夠確實地放出其壓力，同時消除加施加在 葉片上的應力，提昇葉片的可靠性，並且確實地防止過壓 縮狀態發生，而促使性能提昇· 〔用以解決課題之手段〕 爲了達成上述目的，本發明之螺旋葉片式流體機械， 作爲申請專利範圍第1項，係針對具備：汽缸；偏心地配 置在汽缸內，而其一部份接觸在汽缸內面上的滾筒：沿著 此滾筒的周面設置，而從吸入側至吐出側逐漸地縮小間距 的螺旋狀溝：以及出入自由地嵌入此螺旋狀溝中，而將此 螺旋狀溝與汽缸之間的空間，區隔成容積逐漸地從吸入側 往吐出側漸漸變小之複數個作動室的螺旋狀葉片之螺旋葉 片式流體機械，其特徵爲： 在上述螺旋狀溝的吐出側壁面，設置釋放通路，當作 動室內超過規定的壓力時，朝吐出側的作動室放出此壓力 ，且其容積遠比上述作動室小· 作爲申請專利範圍第2項，係針對申請專利範圍地1 項所述之螺旋葉片式流體機械，其中，上述釋放通路，係 爲沿著徑方向設置在面對於吸入側至吐出側的各作動室之 \ φ 螺旋狀溝壁面，且從吸入側至吐出側的各作動室，逐漸地 擴大通路面積：而且，其容稹遠比上述作動室小。 作爲申請專利範圍第3項，係針對申請專利範圍第1 項所述之螺旋葉片式流體機械，其中，上述釋放通路，係 木纸乐尺度ίΐ /丨]中K S家標肀((’NS ) 格（210X297公I ) --11 II ' - - - - . - m n^i t tf 1^1 1^1 nn K 1^1 n^i nn (m f • i^、-°f I w (iilw請背而之注意事項再楨巧本頁) 406165 A7 B7 五、發明说明（4 ) (7?先閱請背而之../1.¾事項再磧艿本頁) 爲沿著徑方向設置在面對於吸入側至吐出側的各作動室之 螺旋狀溝壁面，且從吸入側至吐出側的各作動室，逐渐地 增加通路數；而且，通路之總容積遠比上述馆動室小* 作爲申請專利範圍第4項，係針對申請專利範圍第1 、2或3項所述之螺旋葉片式流體機械，其中，上述釋放 通路之從上述滾筒周面算起的深度，形成比上述螺旋溝狀 的深度還淺· 作爲申請專利範圍第5項，係針對申請專利範圍第1 項所述之螺旋葉片式流體機械，其中，上述作動機構，係 以上述汽缸的中央部作爲邊界，左右對稱地設置2組之成 對式作動機構：而且·上述釋放通路係位於成對式作動機 構之相互達到同樣壓力的同位相之處· ——線 由於具備解決此種課題的手段，在第1項的發明，可 以將規定以上的壓力從作動室放出至吐出側的作動室，並 且使施加在葉片上的過大應力消失，不須對葉片進行特別 加工。 對於專利申.請第2項及第3項的發明*由於愈往髙壓 側的作動室，釋放通路面積愈大：因此，可以促進釋放壓 力，同時，因爲在吸入側也有釋放通路，所以對於在壓縮 過程的較早時期所產生的過壓縮或液壓縮能夠釋放壓力 〇 對於專利申請第4項的發明，在規定以下的一般壓縮 過程中•能夠阻止從所鄰接作動室相互的螺旋狀溝底面之 洩漏。 本纸张尺度这;丨]中UH家標(，NS ) Λ4現格（210X 297公釐） -7 - 406165 A7 ____B7 五、發明説明（5 ) 對於專利申請第5項的發明，在各作動系統達到相同 壓力的時刻可以同時地作釋放，所以各作動系統的壓力不 致成爲不均一· 〔實施形態〕 以下，參照圓面來說明本發明的一實施形態，作爲此 處所揭示的流體機械之螺旋葉片式壓縮機，例如係被用在 空調機的冷凍循環中· 如第1圖所示，在密閉容器1內，大約以密閉容器1 的軸方向中央部爲邊界，在圖的右側部分和左側部分，分 別收容壓縮機構部3和電動機部4· 上述壓縮機構部3，爲兩側端開口的中空筒體，且在 其兩側端的外周面，具有一體地被突設有凸緣部5 a、 5 b之汽缸5 · 上述汽缸5之一端側（圓的左側）的側面，介由固定 具7而被安裝固定有主軸承6 ，閉合汽缸的開口部。而在 他端側（圖的右:側）的側面，介由固定具7被安裝固定有 副軸承8，閉合汽缸的開口部· 沿著此種主軸承6與副軸承8的軸芯*插通曲柄軸9 且被自由回轉地樞支•上述曲柄軸9，不，貫通至主軸承 6與副軸承8之間的汽缸5內，且從主軸承6朝圖的左側 方向突設，構成電動機部4的回轉軸部9 Z · 說明上述曲柄軸9，在上述主軸承6與副軸承8之間 的周面，於相互間隔的位置，一體地設置與曲柄軸軸芯a 本纸依尺度述用中國s家標卑（（，NS ) Λ4規格（210 X 297公釐） --In I - I HX - - - - -1 - — 士^― - ---- m ! . I n HI l— 111 I 1 (邡先閱讀背而之注念事項再^{:,,)本頁) e-ip..-r屮-v^.ir^u 3 消 f Μ .ΐ.印 if _ 406165 :五、發明説明（6 ) 僅偏心規定尺寸e的軸芯b之2個曲柄部9 a 、9b。 圖左側的曲柄部9 a稱爲第1曲柄部、右側的曲柄部 9 b則稱爲第2曲柄部·相互的曲柄部9 a、9 b被形成 爲同一規定寬度· 鄰接於第1曲柄部9 a的更左側之部位’與曲柄軸一 體地被設有配重平衡部9 c ·此配重平衡部9 c ’介由軸 芯而偏心至與上述第1曲柄部9 a的偏心突出方向相反側 的周面部位· 另外，鄰接於第2曲柄部9 b的更右側之部位，被嵌 裝有與曲柄軸9不同體的配重平衡器1 〇 ·此配重平衡器 1 0，偏心至與上述第2曲柄部9 b的偏心突出方向相反 側的周面部位* 在此種曲柄軸9與上述汽缸5之間，介隔有其材質比 鐵的比重還小的例如鋁合金構件之滾筒11。此滾筒11 *爲兩端開口的圓筒體，其軸方向長度與汽缸的軸方向長 度一致· 在滾筒1 1:的內周面形成有階梯狀的內腔部1 2，特 別是與上述曲柄軸9的第1、第2曲柄部9a、9b面對 的部位，形成與這些曲柄部相同寬度，且與回轉自如地與 外周面滑動接觸之第1、第2內腔樞支部12a、12b «· 藉由此構造，滾筒11的軸芯b係與第1、第2曲柄 部9 a·、9 b的軸芯b —致，且對於汽缸5等的軸芯a只 偏心e尺寸•而且，滾筒11的外周壁一部分尺寸被設定 — 1 ----I#------IT------d.. V Λ . (-;>.*/)先間讀背1&之注意事項再填艿本1) 本纸认凡度述用中HS家樣彳{ CNS ) /\4規_格（210X 297公釐） 406165 五、發明説明（7 ) 爲沿著軸方向使其轉接至汽缸5的內周壁一部分· 在上述滾筒1 1的主軸承6側端部與滾筒1 1部位之 間，被介隔設有歐丹（Oldham)機構1 3 *此歐丹機構 1 3調整滾筒1 1的自轉· 在上述滾筒1 1的外周面，設有從副軸承8安裝側端 部至主軸承6安裝側部漸漸地縮小間距之螺旋狀溝1 4， 在此溝中，自由出入地被旋繞有螺旋狀的葉片· 上述葉片1 5，例如使用氟質樹脂的髙滑性材料，其 內徑尺寸形成比滾筒1 1的外徑尺寸還大•亦即，葉片 15係在強制地縮小其直徑的狀態下被嵌入至螺旋狀溝 1 4中；結果，在與滾筒1 1—起被組裝在汽缸5內的狀 態下，葉片1 5的外周齒突出變形使其一直彈性地抵接在 汽缸內周壁上。 沿著上述汽缸5與滾筒11的直徑方向剖面來看，由 於滾筒1 1係在對汽缸5偏心狀態下被收容，且滾筒的周 面的一部份係處於轉接在汽缸上的狀態下，所以在這些汽 缸與滾筒之間形成上弦月狀的空間部。 又，沿著軸方向來看上述空間部，則是在滾筒1 1的 螺旋狀溝14中旋繞葉片：由於其外周面轉接汽缸5內周 壁，所以在滾筒與汽缸之間，利用葉片而舞分隔成複數個 空間部· 這些所被分隔的空間部稱爲作動室1 6 ..........各作 動室1 6的容積，係根據上述螺旋狀溝1 4的間距來決定 ，所以從副軸承8側端部至主軸承6側端部，漸漸地縮小 木纸认尺度进州中SS家標彳（（、NS > Μ現格（210X297公* ) {誚先閱請背而之注意事項再楨巧本I) 訂 線· 10406165 A7 • " -Neighborly China " 巧 ^^ 9 7, Consumption ": ^^ 印 ,, ;; " B7 V. Description of the Invention (1) [Technical Field to which the Invention belongs] The present invention relates to being used Fluid machinery of spiral vane compressors in refrigeration cycle equipment [[Advanced Technology] Compressors that are fluid machinery and constitute refrigeration cycle. In the past, many compressors using reciprocating and rotary methods have been used. The structure of the drive or compression part that transmits the force to the compression mechanism is complicated. • The number of parts is increased. • In addition, check valves are installed on the discharge side to improve compression efficiency. Μ force difference is very large * so gas leaks easily from check valve. In order to solve this problem, it is necessary to improve the dimensional accuracy or assembly accuracy of each part, which results in an increase in manufacturing cost β. Therefore, in recent years, a spiral vane compressor called a fluid compressor has been proposed. This compressor is eccentrically placed in the cylinder as a drum of a slewing body connected to a slewing drive source. The compressor is slewing driven in synchronization with the cylinder. A spiral groove is provided on the peripheral surface of the drum. Free-spiral blades swirling around · A compression chamber is formed between the blade and the peripheral surface of the cylinder and the inner surface of the cylinder as an operating chamber. The refrigerant gas as the operating fluid is drawn into one end of the compression chamber and gradually transferred. Compression to the other end. Therefore, the shortcomings of the conventional compressor can be eliminated, and the sealing can be improved with a simpler structure to achieve efficient compression. At the same time, the manufacturing of parts (read the precautions and read the precautions before filling in. (This page) • 1T line size of this paper; 1] SS family logo Ling (('NS) Λ4 present grid (210X297 mm) __406165 b7__ V. Description of the invention (2) and assembly becomes easier. The problem to be solved] __ However, this type of compressor * uses a spiral shape to determine the compression ratio. At low revolutions or when starting, it will be outside the design compression ratio range and operate at a low compression ratio. Excessive compression will occur in the state, which will significantly reduce the compression performance. In addition, for example, when the air conditioning load is small, there will be a liquid compression phenomenon. The compression chamber will become abnormally high when the pressure exceeds the specified pressure, especially for synthetic resin-based elastic members. Stress is added to the blade, which is likely to cause damage. The abnormal compression state of the compression chamber is certain to occur under certain conditions, and it is unavoidable. • Means must be provided to prevent the damage of the blade even if this state is formed; the applicant of this patent has previously The fluid compressor disclosed in Japanese Patent Laid-Open No. 5-7 1 4 8 2 has been proposed. This technology is characterized in that blades that separate the compression chamber are provided when the pressure during compression exceeds a predetermined pressure. Releasing its pressure to the discharge path of the actuating chamber on the discharge side reduces the stress on the blade. However, if only the discharge path is provided, the thickness of the blade will be reduced, and the blade will be distorted and deformed easily. As a result, the reliability is reduced. As a blade forming method, the blade is first formed into a predetermined shape. The above-mentioned release path is formed by cutting processing, so it is not easy to manufacture. The present invention was developed in view of the above situation, and its purpose is to provide a paper, the size of the prisoner ’s house (CNS > Λ4 specification (210X297 mm) I------1Γ ·. (¾Read the precautions before rewriting this page) .I n ^ i HI 111 I &> _ 1 n mf ml i-V nn ml 1 ^ 1 line -5-406165 A7 _ _ 'B7 ____ V. Description of the invention (3) A spiral vane type fluid machine can reliably release the pressure when the operating chamber is under abnormal pressure for any reason, while eliminating the application The stress on the blades improves the reliability of the blades and reliably prevents the occurrence of an over-compressed state to promote performance improvement. [Means to Solve the Problem] In order to achieve the above-mentioned object, the spiral blade fluid machine of the present invention is applied for The first item of patent scope is for a cylinder that has: a cylinder; an eccentrically arranged cylinder, and a part of which contacts the cylinder inner surface: it is installed along the peripheral surface of the cylinder, and gradually moves from the suction side to the discharge side Ground narrowing spiral Spiral groove: And the spiral groove is freely embedded in and out of the spiral groove, and the space between the spiral groove and the cylinder is divided into a spiral shape of a plurality of operating chambers whose volume gradually decreases from the suction side to the discharge side. The spiral blade type fluid machine of a blade is characterized in that: a release path is provided on the discharge side wall surface of the spiral groove, and when the pressure in the working chamber exceeds a predetermined pressure, the pressure is released to the operating chamber on the discharge side, and the volume is far greater than The above-mentioned operating chamber is small. As the second item of the patent application scope, it is a spiral blade type fluid machine described in the first item of the patent application scope, wherein the above-mentioned release path is provided on the surface in the radial direction from the suction side to the discharge side. Each of the operating chambers on the side has a helical groove wall surface, and each operating chamber from the suction side to the discharge side gradually expands the passage area: Moreover, its capacity is much smaller than the above-mentioned operating chamber. As the third item of the scope of the patent application, it is for the spiral blade type fluid machine described in the first item of the scope of patent application, wherein the above-mentioned release path is the KS family standard 肀 (('NS)) Grid (210X297 Male I) --11 II '----.-Mn ^ it tf 1 ^ 1 1 ^ 1 nn K 1 ^ 1 n ^ i nn (mf • i ^,-° f I w (iilwPlease (Notes on the other side of the page, please repeat this page) 406165 A7 B7 V. Description of the invention (4) (7? Please read the first and back .. / 1 .. ¾ matters and then on this page) is set along the radial direction at The spiral groove wall surfaces of the operating chambers from the suction side to the discharge side are gradually increased, and the number of passages is gradually increased from the suction side to the discharge side. Moreover, the total volume of the passage is much smaller than that of the hall above. Item 4 of the scope of patent application refers to the spiral blade type fluid machine described in item 1, 2, or 3 of the scope of patent application, wherein the depth of the release path from the peripheral surface of the drum is formed more than the spiral groove. The depth is also shallow. As the fifth item in the scope of patent application, it is for the spiral blade type fluid machine described in the first item in the scope of patent application. Among them, The actuating mechanism is based on the central part of the cylinder, and two sets of paired actuating mechanisms are symmetrically arranged left and right: and the release path is located at the same phase where the pairing actuating mechanisms reach the same pressure with each other. ——Because the wire has a means to solve such a problem, in the first invention, it is possible to release more than a predetermined pressure from the actuating chamber to the actuating chamber on the discharge side, and to eliminate the excessive stress applied to the blade. The blades are specially processed. For the patent application, please invent the 2nd and 3rd inventions * As the actuating chamber on the pressure side becomes more, the area of the release path is larger: Therefore, the release pressure can be promoted. At the same time, because there is also on the suction side, The release path allows pressure to be relieved from over-compression or fluid compression generated earlier in the compression process. For the invention of patent application No. 4, in the general compression process below specified, it can prevent each other from adjoining operating chambers. The leakage of the bottom surface of the spiral groove. This paper scales this; 丨] UH house standard (, NS) Λ4 is present (210X 297 mm) -7-406165 A7 ____B7 V. Description of the invention (5) For the invention of item 5 of the patent application, the pressure can be released at the same time when the actuation systems reach the same pressure, so the pressure of each actuation system does not become uneven. [Embodiment] Below, refer to A circular surface is used to describe an embodiment of the present invention. As a spiral vane compressor of a fluid machine disclosed herein, for example, it is used in a refrigeration cycle of an air conditioner. As shown in FIG. 1, in a closed container 1, Approximately, the axial center portion of the closed container 1 is a boundary, and the compression mechanism portion 3 and the motor portion 4 are accommodated in the right and left portions of the figure. The compression mechanism portion 3 is a hollow cylinder with open ends on both sides, and On the outer peripheral surfaces of both side ends, there is a cylinder 5 integrally provided with flange portions 5 a and 5 b. The side surface of one end side (the left side of the circle) of the cylinder 5 is mounted and fixed through a fixture 7. There is a main bearing 6 which closes the opening of the cylinder. On the side of the other end (right: side in the figure), a secondary bearing 8 is fixed via a fixture 7 and the opening of the cylinder is closed. Along the axis of the main bearing 6 and the secondary bearing 8, the shaft is inserted. The crank shaft 9 passes through and is pivotally supported freely. The above-mentioned crank shaft 9 does not penetrate into the cylinder 5 between the main bearing 6 and the auxiliary bearing 8 and protrudes from the main bearing 6 to the left in the figure to constitute a motor. Rotary shaft section 9 Z of section 4 · The crank shaft 9 will be described. The peripheral surface between the main bearing 6 and the auxiliary bearing 8 is integrally provided with the crank shaft core a at a spaced position from each other. Use Chinese s family standard ((, NS) Λ4 specification (210 X 297 mm) --In I-I HX-----1--^^------ m!. I n HI l — 111 I 1 (邡 read the memorabilia first and then ^ {: ,,) this page) e-ip ..- r 屮 -v ^ .ir ^ u 3 eliminate f Μ .ΐ. 印 if _ 406165 V. Description of the invention (6) Only the two crank parts 9a, 9b of the shaft core b of the eccentric predetermined size e. The crank part 9 a on the left is called the first crank part, and the crank part 9 b on the right is called the second crank part. The mutual crank parts 9 a and 9 b are formed to have the same predetermined width and are adjacent to the first crank part. The left side portion of 9 a is provided with a weight balance portion 9 c integrally with the crank shaft. This weight balance portion 9 c 'is eccentric to the eccentric protruding direction from the first crank portion 9 a through the shaft core. Opposite peripheral surface area · In addition, a weight balancer 1 which is different from the crank shaft 9 is fitted in a portion further to the right of the second crank portion 9 b. This weight balancer 10 is eccentric. To the peripheral surface on the side opposite to the eccentric protruding direction of the second crank portion 9 b * Between the crank shaft 9 and the cylinder 5 described above, a material having a smaller specific gravity than iron is interposed, for example, an aluminum alloy member Drum 11. This roller 11 * is a cylindrical body with open ends, and its axial length is consistent with the axial length of the cylinder. A stepped inner cavity portion 12 is formed on the inner peripheral surface of the roller 1 1: especially with the crank The first and second crank portions 9a and 9b of the shaft 9 face the first and second inner cavity pivot support portions 12a and 12b having the same width as these crank portions and sliding contact with the outer peripheral surface freely. · With this structure, the shaft core b of the drum 11 is the same as the shaft core b of the first and second crank portions 9 a, 9 b, and the shaft core a of the cylinder 5 and the like is only eccentric with the dimension e. Part of the size of the outer peripheral wall of the drum 11 is set — 1 ---- I # ------ IT ------ d .. V Λ. (-; ≫. * /) Read back 1 & amp Note for re-filling of this book 1) This paper recognizes the HS home samples used in the description {CNS) / \ 4 规 _ 格 (210X 297mm) 406165 V. Description of the invention (7) is along the axis It is transferred to a part of the inner peripheral wall of the cylinder 5. The Oldham mechanism 1 3 is interposed between the end of the main bearing 6 side of the above-mentioned drum 11 and the part of the drum 11 1 * This Oudan mechanism 1 3 Adjust the rotation of the roller 1 1 On the outer peripheral surface, there are spiral grooves 1 4 that gradually reduce the distance from the mounting side end of the auxiliary bearing 8 to the mounting side of the main bearing 6. In this groove, spiral blades are spirally wound freely in and out. The blade 15 is made of, for example, a slippery material made of a fluororesin, and its inner diameter is larger than the outer diameter of the drum 11. That is, the blade 15 is embedded in a state where its diameter is forcibly reduced. As a result, the spiral grooves 14 are assembled in the cylinder 5 together with the rollers 11. As a result, the outer teeth of the blades 15 protrude and deform so as to elastically abut against the inner peripheral wall of the cylinder. Looking at the diameter section of the cylinder 5 and the drum 11, as the drum 11 is accommodated in an eccentric state with respect to the cylinder 5, and a part of the peripheral surface of the drum is transferred to the cylinder, Therefore, a crescent-shaped space portion is formed between these cylinders and the drum. In addition, when the space portion is viewed along the axial direction, the blade is wound in the spiral groove 14 of the drum 11: the outer peripheral surface of the cylinder is transferred to the inner peripheral wall of the cylinder 5, so the blade dances between the drum and the cylinder. Divided into a plurality of space parts · These divided space parts are called operating chambers 16 ..... The volume of each operating chamber 16 is determined according to the pitch of the spiral groove 14 Therefore, from the end of the auxiliary bearing 8 side to the end of the main bearing 6 side, gradually reduce the size of the paper and paper into the SS family standard in the state 彳 ((, NS > Μ 现 格 (210X297 公 *) { Note from the back and then copy this book I) Threading · 10
A 7 406165 B7 五、發明説明（8 ) 容積· 而且*在各作動室1 6 .........中，分別設有後述的釋 放通路2 0 · 在上述密閉容器1側部·貫通設置用來連接構成冷凍 循環的蒸發器之吸入管1 7 :在密閉容器1內部，被連接 至設在上述副軸承8上的連接部8 a ·此連接部8 a，對 於被設在汽缸凸緣部5 b的凸陷部1 9開口，而與被設在 汽缸5端部外周面上的緩衝部21連通· 在上述主軸承6的側面部，設有吐出用孔2 4 ·介由 此吐出用孔，連通汽缸5和滾筒1 1側端空間部 < 以及電 動機部4側的空間部* 由於上述螺旋狀溝1 4的間距之設定，所以設置上述 緩衝部2 1之一側的作動室1 6形成爲吸入部A :設置與 此相反側的吐出用孔2 4之一側的作動室1 6則形成爲吐 出部B。 形成被上述主軸承6與曲柄軸9及滾筒1 1所圍繞的 第1空間部25;形成被曲柄軸9與滾筒所圍繞的第2空 間部2 6 :且形成被副軸承8與曲柄軸9及滾筒1 1所圍 繞的第3空間部2 7 · 從上述曲柄軸9的副軸承8側端面至作爲中途部之主 軸承6的樞支部分，沿著曲柄軸的軸芯，設置導引用孔 2 8 ·此導引用孔2 8的開口端與副軸承8的軸樞支部開 口端，係藉由以固定具2 9而被安裝在副軸承端面上的堵 塞板30而被堵塞* 本紙凡尺度这用中KS家標彳（（’NS ) Λ4規格（210X297公釐） ,. i ~¾1-IT—r 線 (計先閱請背而之注意事項再ISCTt?本頁) 406165 五、發明説明（9 ) 上述導引用孔2 8與曲柄軸9外周面及各軸承6、8 ，係利用複數個氣體用孔3 1、32而被連通•在汽缸凸 綠部5 3之圖的上部側，設置貫通兩側面的氣體導引孔 4 3· 上述電動機4，係由：被嵌裝在從主軸承6突出之曲 柄軸9的回轉軸部9 Z上的滾筒4 5、以及和此滾筒的外 周面隔開規定的間隙而被嵌裝在上述密閉容器1之內周面 上的定子46所構成· 上述釋放通路2 0 *如第1圓及第2圖所示，被設在 形成於滾筒1 1之螺旋狀溝1 4的每1螺旋（螺旋位置角 3 6 0° )之位置的螺旋狀溝14壁面•若再作說明，各 釋放通路2 0，係面對於各作動室，只被設在吐出部B側 的壁面。 而且•釋放通路2 0，大致形成剖面爲半圓狀，一端 部係開口於滾筒1 1的周面*他端部則形成與螺旋狀溝 14底面幾乎一致，而延著滾筒11的直徑方向設置* 如此構成的螺旋葉片式壓縮機，通電至電動機部4後 ，一體回轉驅動轉子4 5和曲柄軸9 ·此曲柄軸9的回轉 力，經由第1 、第2曲柄部9a、9b，傅達至滾筒11 〇 亦即，曲柄部9 a、9 b被設置成偏心，由於滾筒 1 1的內腔樞支部12a、12b旋轉自如地卡合於此， 所以滾筒1 1被推壓到曲柄部•而且，被架設在曲柄軸9 與滾筒1 1之間的歐丹機構1 3，控制滾筒的自轉，所以 本紙认尺度述用中囚K家標呤（（’NS ) Λ4規格（2丨0X297公犮） "先閱讀背而之注意事項再^'巧本頁) *vs 線 -12 - itiiuas 五、發明説明（10 ) A7 B7 滾 筒 1 3 形 成 公 轉 運 動 • 另 外 從 吸 入 管 1 7 在 汽 缸 5 與 滾 筒 1 1 所 形 吸 入 部 A 側 的 作 動 室 1 6 隨 著 滾 筒 1 1 的 公 轉 之 轉 接 位 置 逐 漸 朝 圓 周 方 溝 1 4 進 行 出 入 動 作 • 亦 作 突 出 / 沒 入 移 動 • 被 引 導 至 吸 入 部 A 側 片 1 5 形 成 螺 旋 狀 所 以 地 被 移 送 至 吐 出 部 B 方 向 上 述 葉 片 1 5 被 設 定 小 間 距 以 此 種 葉 片 所 分 小 所 以 冷 媒 氣 體 在 作 動 t 而 在 最 後 的 吐 出 部 B 側 成 髙 壓 化 9 髙 壓 氣 體 從 吐 出 部 B r·]· 空 間 部 2 5 後 t 經 由 設 在 t 導 至 電 動 機 部 4 側 的 空 間 -小· ：r 凸 緣 部 5 a 上 的 氣 體 導 引 π j .·；·>· 部 3 側 的 空 間 部 • 山 IV A 由 於 吐 出 管 1 8 的 開 1ι if 印 f · 氣 體 被 導 至 吐 出 管 1 8 • •ί· 再 者 上 述 釋 放 通 路 木紙ίί<·Κ度中家標彳（（'NS ) Λ4規格（2]〇Χ297公釐） 吸入的低壓冷媒氣體•暫時儲存 成的緩衝部2 1內*然後被導至 〇 運動，對於滾筒的汽缸5內周面 向移動，葉片1 5則對於螺旋狀 即•葉片15朝滾筒的直徑方向 的作動室1 6之冷媒氣體，因葉 隨著滾筒1 1的公轉運動而依序 的作動室1 6 · 爲從吸入部至吐出部B側逐漸縮 隔的作動室16之容積因逐漸縮 室之間依序地被移送之間被壓縮 的作動室內上昇至規定壓力且變 的作動室1 6吐出，充滿在第1 主軸承6的吐出用孔24·被引 部內。然後經由被設在汽缸5的 孔4 3 ，引導且。充滿於壓縮機構 口端與此空間部相對，所以髙壓 再被導出至凝縮器· 2 0 ，在以下的狀態下爲有作用 ----Μ----------IT-------年 - I (計先閱讀背而之注意事項再硝巧木页) -13 - __406165 B7___ 五、發明説明（π ) *亦即，如第3 (A)圖所示，在通常的壓縮過程中，吐 出部B被形成在圖的左側部位，吸入部A被形成在右側部 位，所以左側的作動室1 6 b處於比右側的作-動室1 6 a 還高壓的狀態· 因此，與螺旋狀溝卡合的葉片1 5，壓力係施加在圖 的左側面，而被推壓使其密著於螺旋狀溝的右側面•區隔 作動室1 6 b的葉片1 5，被推壓在所鄰接作動室1 6 a 側（吸入部A側）的壁面，同時被推壓在與所鄰接作動室 1 6 c相反側的壁面：亦即，被推壓在與被設在該吐出部 B側的釋放通路2 0相反側的側面· 從上述葉片的旋繞始端至旋繞終端被同樣地形成，因 此各作動室1 6的密閉確實地形成· 當不明原因的狀況造成過壓縮狀態，會有作動室 16b的壓力超過規定壓力的情況。此時，如第3 (B) 圖所示，區隔作動室1 6 b的葉片被推壓至左右邊鄰接的 作動室1 6 a ' 1 6 c側。 亦即，葉片1 5被推壓在吸入部A側的作動室1 6 a 側，與正常壓縮作用時相同而沒有改變。相對於此，鄰接 作動室1 6 c側的葉片1 5，被密著地推壓在設於該作動 室1 6 b的吐出部B側之釋放通路2 0上、，因此，葉片 15變成從位於正常的密接狀態下的釋放通路對面的壁面 離開，而在此壁面和葉片1 5之間形成間隙· 在異常高壓狀態的作動室1 6 b內，從螺旋狀溝1 4 的壁面與葉片1 5之間的間隙，髙壓的氣體放出至作動室 本纸认尺度述州中因囚家標彳（（’吣）/\4規格（210父：297公犮) ~ -14 - (对先間讀背而之注意事項再項巧本頁) 406165 •v-f'' 五、發明説明（12 ) 1 6 c側的螺旋狀溝1 4內•因此在螺旋狀溝1 4內形成 釋放通路2 0 *所以髙壓氣體經由此釋放通路被導至吐出 部B側的作動室1 6 c * 結果，進行壓力控制來使形成異常高壓狀態之作動室 1 6 b的壓力立即下降，達到防止壓力損失，且不致造成 對葉片1 5施加過大的負載，保持可靠性。 上述釋放通路，亦可爲以下所述的構成· 如第4圖所示，在螺旋狀溝1 4的壁面上分別設置面 對各作動室（未圖示）之釋放通路20a、20b、 2 0c .....不過，對於各釋放通路20a…，係從吸入 部A側至吐出部B侧的作動室，其通路面積逐漸擴大· 若加以說明，由於各釋放通路2 0 a…的剖面形成爲 半圓狀，所以釋放通路的直徑寬度D、E、F…，從吸入 部A側至吐出部B側的作動室，逐漸變大。 若爲此種釋放通路2 0 a…的構成，由於在吸入側也 有釋放通路2 0 a，所以對於在壓縮過程初期所產生的過 壓縮乃至於液壓縮，也能夠極有效地使壓力下降· 再者，未圓示的釋放通路的徑寬D、E、F…，其寬 度也可以全部相同· 如第5圖所示，也可以從吸入部A側至吐出部B側的 作動室，逐漸增加設置在螺旋狀溝1 4壁面上而面對各作 動室（未圖示）的釋放通路2 0個數•當然，各釋放通路 的面積相同· 此種釋放通路2 0的構成•同樣地能夠有效地降低過 (对先閱讀背而之注意事項再填巧本頁) " m -I—-I ml .，-0^-7 本纸认尺度i4;f!中Sg家標彳（rNS ) ( 210X 297公釐） -15 - 40(3 65 ABl 五、發明説明（13 ) 壓縮乃至於液壓縮時之壓力 也可以應用於第6圖所 在密閉容器50內•收 5 2 ·上述壓縮機構部5 1 置有滾筒活塞（以下，稱爲 上述滾筒5 4，其兩端 至固定在密閉容器5 0的內 的樞支孔部內，而樞支成能缸5 3 另一方面，在汽 示的螺 容壓縮 ，係爲 滾筒） 的軸部 壁之主 夠回轉 的兩端 屮 4\ i3 J 消 f·， A H 印 裝有以金屬 主軸承5 5 ，僅從上述 滾筒5 4之 5 3的回轉 此處， 被稱爲第1 缸軸承5 8 只在第 路G被用作 有該吐出通 6 5· 第1、 環狀*上述 沿著該軸方 所形成 和副軸 汽缸5 間•被 力傳達 位於圖 汽缸軸 則被稱 2汽缸 爲吐出 路G側 的汽缸 承5 6 3的軸 隔設有 至滾筒 的右側 承。位 爲第2 軸承5 通路， 的密閉 軸承5 7 外周之間 心偏心e 回轉力傳 5 4。 之主軸承 於圖的左 汽缸軸承 8上設置 所以稱爲 容器5 0 旋葉片 機構部 在汽缸 5 4· 5 4a 軸承5 自如· 內徑上 、5 8 •上述 •而且 達機構 式壓縮機· 5 1與電動機部 5 3內，偏心配 、5 4 b被插入 5與副軸承5 6 ，分別被壓入嵌 ，分別被介隔在 滾筒5 4的軸心 ，在汽缸5 3與 6 6，使汽缸 第2汽缸軸承57、5 吐出通路G，在第2汽 向，形成一對設置在汽 5 5側的汽缸軸承5 7 側之副軸承5 6側的汽 • 氣體通路G。此氣體通 吐出通路•而且，在設 的周壁上，設置吐出管 8，被形成厚度較大的 缸軸承5 8的厚度部， 缸軸承的軸心對稱位置 1^---Μ----I#------訂-------線. ("先閱請背而之注意事項再"«?本頁) 本纸张尺度述州中^囚家標彳（ns's }八4故格（210X297公釐} -16 - A7 ___ 406165 B7____ 五、發明説明（14) 處之的孔部· 在上述密閉容器5 0的一側面連接有吸入管5 9，連 通至的吸入導引通路6 0被設在主軸承5 5中。此導引吸 入通路6 0，係從滾筒軸部5 4 a的一端面，沿著此軸方 向設置，進而連通至滾筒軸部54a 、54b相互之間的 滾筒本體5 4 c的端部外周面所開口的吸入通路6 1 · 在上述滾筒本體5 4 c的周面，形成從一端側至他端 側漸漸縮小間距的螺旋狀溝6 2 *在此溝中，出入自由地 嵌入螺旋狀的葉片6 3。因此，汽缸5 3內周面與滾筒 5 4周面之間的空間，藉由上述葉片6 3而被分隔成複數 個，從這些空間的一端側至他端側，亦即從吸入部A側至 吐出部B側，形成漸漸地縮小容積之複數個作動室6 4… 〇 在面對這些作動室6 4之螺旋狀溝6 2的吐出部B側 壁面，分別設有與先前所述之葉片式壓縮機的釋放通路 2 0相同形態之釋放通路2 0A · 不過，在此處將各釋放通路2 0 A，螺旋位置角特定 在3 6 0 °以下· 以此種構成的壓縮機，隨著通電至電動機部5 2，而 回轉汽缸5 3 *汽缸的回轉力經由回轉傳達機構6 6傳達 至滾筒54 *汽缸53與滾筒54，因相互之間的半徑不 同，以相對的圓周速度，且保持原來的位置關係同步地回 轉· 隨著汽缸5 3與滾筒5 4的回轉，葉片6 3相對於螺 本纸张尺度竓州中S S家標( CNS ) Λ4ί^ ( 210 X297^«· ) ~ ~ I J---Μ----.------訂-------線· ("先閱讀背而之注意事項再靖巧本页) 附件1第86107428號專利申請案 中文說明書修正頁 A7 B7 民國88年10月修 五、發明說明（ 煩請委員明示 ;\‘：原實質内容 經濟部智慧財產局員工消費合作社印製 15 旋狀溝6 2出入，朝滾筒的直徑方向突出/沒入。於是， 冷媒氣體從吸入管5 9吸入，經由被形成在主軸承5 5的 導引通路6 0 '及被設在滾筒5 4的吸入通路，被導至汽 缸5 3內β 而且’被吸入汽缸5·*3內的冷媒氣體，從各作動室 6 4當中最位於吸入部A側的作動室6 4，依順被移送至 最位於吐出部B側的作動室6 4。進而，冷媒氣體在這些 作動室6 4之間依序地被移送時，漸漸地被壓縮。 在被移送至吐出部B側的最後一個作動室之時，上昇 至規定壓力，從此處沿著第2汽缸軸承5 8的吐出通路G 而被導引。然後，高壓器體從吐出通路G吐出至密閉容器 5 ◦內，在此容器內一旦充滿後便被導至吐出管6 5 ，且 被導出至外部的冷凍循環機器中。 針對此種螺旋葉片式壓縮機，當作動室6 4形成過壓 縮狀態時，被設在該作動室的吐出部B側之釋放通路 2 OA從葉片6 3開放時，導引高壓氣體。 因此，高壓氣體從該作動室6 4經由各釋放通路 2 OA依序地被導引至吐出部B側的作動室6 4內，最終 形成從吐出部B側的最後一個作動室經由吐出通路G而被 導引至密閉容器5 0內，迅速地降低壓力而抑制過壓縮所 造成的損失，變成安定的壓縮作用。 第7圖係以具備先前在第6圖所述之螺旋葉片式的壓 縮機構部5 1爲前提，以汽缸53A的中央部作爲邊界* 左右對稱地設置2系統之壓縮機構部5 1 A、5 1 B，稱 本紙張尺度適用中國國家標準（CNS)A4規格（210 x 297公釐） (請先閱讀背面之注意事項再锣寫本頁) -装--------訂---------. 18 — 406：65a7 ___ B7五、發明説明（16 ) 爲所謂的成對式壓縮機·（再者，由於此壓縮機係以第6 圖所說明過的壓縮機爲基本構造，所以在此處省略其詳細 構成作用的說明）· - 在各作動室6 4的吐出部B側的壁面上，設有釋放通 路20B ·亦即，對於各系統的壓縮機構部5 1A、 5 1B，具備相互同相位的釋放通路20B · 各系統的壓縮機構部5 1A、5 1B，具備上述釋放 通路2 Ο B所形成的作用效.果，係與先前第1圖及第6圖 所說明之螺旋葉片式壓縮機完全相同。 並且，對於具備此種成對式的壓縮機構部5 1 A、 5 1 B的壓縮機，因在兩方壓縮機構部之同相位的位置處 ，設置上述釋放通路2 Ο B ·所以從各壓縮機構部系統達 到相同壓力的時刻•同時開始高壓下降作用· 因此，在兩方的壓縮機構部5 1 A、5 1 B系統的壓 縮過程中，不會有壓力不均衡，可以得到安定的壓縮性能 •而且，由於沒有壓力不均衡，所以滾筒5 4 A不會朝任 何一方的推力方向移動，也不會碰撞軸承等其他零件而產 生噪音。 如第8圖所示，由於將釋放通路2 0 C的深度L (亦 即從滾筒11圓周面至釋放通路底面的尺寸），設定爲比 1 螺旋狀溝1 4的深度（亦即從滾筒1 1的圓周面至螺旋狀 溝底面的尺寸）還淺（L<D)，在通常的壓縮狀態下， 防止氣體經由釋放通路2 0 C從螺旋狀溝1 4的底面洩漏 至所鄰接的作動室內· 本％依乂度述 m t ( CNS ) /\4^m ( 210X297/^^ ) I ---M----I·"------訂------银. - (ii先間讀背而之注¾事項再硝1ΛΤ本頁) 經濟部智慧財產局員工消費合作社印製 A7 B7_ 五、發明説明（17 ) 如第9圖所示•將釋放通路2 0D的寬度（直徑）設 爲X，螺旋狀溝1 4的底部直徑設爲4 d 0時•設定爲成 立XS0.6d0的關係· : 而且，實際上作成釋放通路2 Ο E)的工具（削刀） 6 5，原樣地使用作成螺旋狀溝20D的工具•亦即•切 削滾筒1 1的圓周面而設置螺旋狀溝1 4後，不用更換工 具，便可以變換成切削釋放通路2 0D · 因此，能省略工具的更換手續·同時不會有由於工具 更換所造成煩雜的定位· 再者*以上所說明過的作動機械，係全部具備螺旋葉 片式的壓縮機，但並不限於此*也可以應用在具備螺旋葉 片式的泵機構之泵· 〔發明之效果〕 如以上所述，依據申請專利範圔第1項之發明，在螺 旋狀溝的吐出側壁面設置釋放通路，當作動室內超過規定 壓力時，因爲將此壓力放出至吐出側的作動室*所以施加 在葉片上的過大應力消失，可以從作動室確實地放出規定 以上的壓力•有效地達到防止髙壓降低所造成的壓力損失 ，達到提昇可靠度的效果· 依據申請專利範圍第2項之發明，將釋放通路面對各 作動室，且從吸入側至吐出側的各作動室，逐漸地擴大通 路面積。依據申請專利範圍第3項之發明，釋放通路從吸 入側至吐出側的作動室，逐漸增加通路數· 本紙張尺度適用中國國家標準（CNS ) A4規格（210Χ297公釐） -20 - m-^n nn Tten I 1^1 nJ nn Mm In mt m ^ r 1 ·ϋ^ϋ 4 (請先閱讀背面之注意事項再填寫本頁) - · ""•Τ 屮"J:!v-^:u lv'-;,:fA” ：；；：：.. A7 B7 五 '發明説明（18 ) 因此，依據申請專利範圍第2項及第3項之發明，愈 往高壓側的作動室，其釋放通路面積愈大，因此對於在壓 縮過程早期所產生的過壓縮或液壓縮，也能確實地釋放壓 力· 依據申請專利範圍第4項，將釋放通路的深度，形成 爲比螺旋狀溝的深度還淺，在通常狀態的壓縮過程，能夠 確實地阻止從所鄰接作動室相互的螺旋狀溝底部洩漏。 依據申請專利範圍第5項，作動機構係以上述汽缸的 中央部爲邊界，設置成左右對稱的成對式，因爲釋放通路 係在成對式作動機構之相互達到同樣壓力的同位相之處， 所以在兩作動機構系統之間不會有壓力的不均衡，能夠得 到安定的壓縮性能· 〔圖面之簡單說明〕 第1圖係表示本發明之一實施形態的流體機械之螺旋 葉片式壓縮機的縱剖側面圖· 第2圖係相同實施形態之在螺旋狀溝中旋繞有葉片之 滾筒的立體圖· 第3 (A)圖係表示在相同實施形態之正常壓縮過程 中的葉片與螺旋狀溝的關係之說明圖。 > , 第3 (B)圖係在過壓縮狀態下之說明圖· 第4圖係其他實施形態的滾筒之部分立體圖· 第5圖係另外的實施形態的滾筒之部分立體圖。 第6圖係爲另外的實施形態的螺旋葉片式壓縮機之縱 本紙浓尺度ii ；n ( ('NS ) Λ4^ ( 210X 297^* ) ~ -21 - (誚先閱請背而之注意事項4填』,;木頁) ¾ TJ '-β A7 B7 406165 五、發明説明（19 ) 剖側面圖* 第7圓係爲另外的實施形態的螺旋葉片式壓縮機之縱 剖側面圖· 二 第8圖係爲另外的實施形態的滾筒之部分立體圓· 第9圖係爲另外的實施形態的滾筒之部分立體圖· 第10(A)(B)圖係分別表示一般之壓縮行程及過壓縮狀態之圖。 〔圖號說明〕 5、5 0 :汽缸 11、54、54A:滾筒 14、62 :螺旋機構 1 6、6 4 :作動室 1 5、6 3 :葉片 3、51、51A、51B:作動機構部 20、20A、20B、20C、20D :釋放通路 ί. -VI! ^^^1 -·*-= nn In i nn 1 -士 - I I li SI— 一 J ^^、T (請先閱讀背面之注意事項再填寫本頁) * . 經濟部智慧財產局員工消費合作社印製 本紙張尺度適用中國國家標準（CNS ) A4規格（210'乂297公釐）A 7 406165 B7 V. Description of the invention (8) Volume · And * in each of the operating chambers 16 ........., a release passage 2 0 described later is provided on each side of the hermetic container 1 · A suction pipe 17 is provided through to connect the evaporator constituting the refrigeration cycle. Inside the sealed container 1, it is connected to a connecting portion 8a provided on the auxiliary bearing 8. The connecting portion 8a is provided for the cylinder The convex portion 19 of the flange portion 5 b is opened, and communicates with the buffer portion 21 provided on the outer peripheral surface of the end portion of the cylinder 5. The side surface of the main bearing 6 is provided with a discharge hole 2 4. This ejection hole communicates with the cylinder 5 and the roller 11 1 side end space portion < and the motor portion 4 side space portion * Because the pitch of the spiral groove 14 is set, one side of the buffer portion 21 is provided The operating chamber 16 is formed as a suction section A: The operating chamber 16 provided on one side of the discharge hole 24 on the opposite side is formed as a discharge section B. Forming a first space portion 25 surrounded by the main bearing 6 and the crank shaft 9 and the drum 11; forming a second space portion 2 6 surrounded by the crank shaft 9 and the drum: and forming a secondary bearing 8 and the crank shaft 9 And the third space portion 2 7 surrounded by the roller 11 1 · A guide hole is provided along the shaft core of the crank shaft from the end face of the auxiliary bearing 8 side of the crank shaft 9 described above to the pivot support portion of the main bearing 6 as a halfway portion 2 8 · The open end of this guide hole 2 8 and the open end of the pivot support of the auxiliary bearing 8 are blocked by the blocking plate 30 which is fixed on the end surface of the auxiliary bearing with the fixing tool 29. This uses the KS family standard 彳 (('NS) Λ4 size (210X297 mm),. I ~ ¾1-IT-r line (count the precautions before reading first, then the ISCTt? This page) 406165 V. Description of the invention (9) The above-mentioned guide holes 28 and the outer peripheral surface of the crank shaft 9 and the bearings 6 and 8 are connected by a plurality of gas holes 3 1 and 32. • On the upper side of the figure of the cylinder convex green portion 53, Gas guide holes 4 3 through both sides are provided. The above-mentioned motor 4 is fitted to a rotary shaft portion 9 Z of a crank shaft 9 protruding from the main bearing 6. The rollers 4 and 5 and the stator 46 embedded in the inner peripheral surface of the hermetic container 1 are separated from the outer peripheral surface of the roller by a predetermined gap. The release path 2 0 * As in the first circle and the second As shown in the figure, the wall surface of the spiral groove 14 is provided at each spiral position (spiral position angle 360 °) of the spiral groove 14 formed in the drum 11. If it is explained, each release path 20 For each actuating chamber, the surface is only provided on the wall surface on the side of the ejection part B. Also, • the release path 20 is formed in a semicircular cross section, and one end is opened on the peripheral surface of the drum 11 * the other end is formed It is almost the same as the bottom surface of the spiral groove 14 and is arranged along the diameter direction of the drum 11. The spiral vane compressor configured in this way is driven to the motor unit 4 and rotates the rotor 45 and the crankshaft 9 as a whole. This crankshaft 9 The turning force of the crankshaft is passed through the first and second crank parts 9a and 9b to reach the roller 11 〇 That is, the crank parts 9 a and 9 b are set to be eccentric. Since the inner cavity pivots 12a and 12b of the roller 11 rotate, Freely engages here, so the roller 11 is pushed against the crank The Oudan mechanism 1 3 between the crank shaft 9 and the drum 11 controls the rotation of the drum, so the paper's recognition standards are described in the prisoner's standard (('NS) Λ4 specification (2 丨 0X297)) " First Read the precautions on the back again ^ 'Qiao page) * vs line-12-itiiuas V. Description of the invention (10) A7 B7 Drum 1 3 Forms a revolution movement • In addition, the suction pipe 1 7 is in the cylinder 5 and the drum 1 1 The operating chamber 1 on the side of the suction section A 6 gradually moves in and out of the circumferential square groove 1 4 as the transfer position of the revolution of the drum 1 1 • Also protrudes / submerged. • It is guided to the side section of the suction section 1 5 The spiral shape is transferred to the discharge section B. The above-mentioned blades 15 are set at a small pitch. The size of this blade is small, so the refrigerant gas is actuated at the last discharge section B side. Discharge part B r ·] · Space part 2 5 After t leads to motor via t Space on the side of the machine part 4-Small: r Gas guide on the flange part 5 a π j ···· > · The space part on the side of the part 3 • Mountain IV A due to the opening of the discharge pipe 1 8 if 印f · The gas is led to the discharge pipe 1 8 • • ί Further, the above-mentioned release path wood paper ί < · K Degree House Standard 彳 (('NS) Λ4 specification (2) 0 × 297 mm) Inhaled low-pressure refrigerant gas • The temporarily stored buffer section 2 1 * is then guided to 0 movement. For the cylinder 5 of the drum, the inner peripheral surface moves, and the blades 15 are spiral. That is, the blades 15 act in the diameter direction of the drum. As the refrigerant gas, the operating chambers 16 are sequentially moved by the leaves in accordance with the orbital movement of the drum 11. The volume of the operating chambers 16 which are gradually narrowed from the suction part to the B side of the discharge part are sequentially sequentially The operating chamber compressed during the transfer rises to a predetermined pressure and changes and the operating chamber 16 is discharged, and is filled in the discharge hole 24 and the lead portion of the first main bearing 6. It then guides through the hole 4 3 provided in the cylinder 5. The filling end of the compression mechanism is opposite to this space part, so the pressure is again led to the condenser · 2 0, which is effective in the following states ---- M ---------- IT- ------ Year-I (Count down the precautions before reading the pages) -13-__406165 B7___ V. Description of the invention (π) * That is, as shown in Figure 3 (A), In the normal compression process, the discharge portion B is formed on the left side of the figure, and the suction portion A is formed on the right side. Therefore, the left operating chamber 16 b is at a higher pressure than the right operating chamber 16 b · Therefore, the pressure of the blade 15 engaged with the spiral groove is applied to the left side of the figure, and the pressure is pushed to make it close to the right side of the spiral groove. • The blade 1 5 that separates the operating chamber 1 6 b , Is pushed against the wall surface of the adjacent operating chamber 16 a side (suction section A side), and at the same time is pushed against the wall surface of the opposite operating chamber 1 6 c side: that is, pushed against the The side surface on the opposite side of the release passage 20 on the side of the ejection portion B is formed similarly from the winding start end to the winding end of the blade, so that the airtightness of each operation chamber 16 is reliably formed. • When unexplained condition caused by over-compressed state, there will be pressure operation chamber 16b exceeds the predetermined pressure situation. At this time, as shown in FIG. 3 (B), the blades that separate the operating chamber 16b are pushed to the sides of the operating chambers 16a'16c adjacent to the left and right sides. That is, the blades 15 are pushed against the operation chamber 16 a side of the suction part A side, which is the same as in the case of normal compression, without change. On the other hand, the blades 15 adjacent to the operation chamber 16 c side are closely pressed against the release path 20 provided on the discharge portion B side of the operation chamber 16 b. Therefore, the blade 15 becomes The wall surface opposite to the release path in the normal tight state is separated, and a gap is formed between the wall surface and the blade 15. In the operating chamber 1 6 b in an abnormally high pressure state, the wall surface of the spiral groove 14 and the blade 1 The gap between 5 and the pressure of the gas is released to the paper of the operating room. According to the standard of prisoners in the state (('吣) / \ 4 size (210 father: 297 male)) ~ -14-(to the first Note from time to time, please refer to this page again) 406165 • v-f '' V. Description of the invention (12) 1 6 c-side spiral groove 1 4 • Therefore, a release path is formed in the spiral groove 14 2 0 * So the pressurized gas is led to the actuating chamber 1 6 c on the side of the discharge part B through this release path. As a result, the pressure is controlled to immediately reduce the pressure of the actuating chamber 16 b forming an abnormally high pressure state to prevent the pressure. Loss without causing excessive load on the blade 15 to maintain reliability. The above release path can also The structure is described below. As shown in FIG. 4, on the wall surface of the spiral groove 14, release passages 20a, 20b, and 20c facing each operation chamber (not shown) are provided. For each of the release paths 20a ..., the actuating chambers from the suction part A side to the discharge part B side are gradually enlarged in the passage area. If explained, since the cross sections of each release path 20a ... are formed into a semicircular shape, the release The diameter width D, E, F of the passage gradually increases from the actuating chamber on the suction side A to the discharge side B. With this configuration of the release passage 2 0 a ..., there is also a release passage 2 on the suction side. 0 a, so for the over-compression and even liquid compression generated at the beginning of the compression process, the pressure can be reduced very effectively. Furthermore, the diameters D, E, F of the uncircumscribed release path are also wide. It can be all the same. As shown in Fig. 5, the operating chambers from the suction part A side to the discharge part B side can be gradually increased to be provided on the wall surface of the spiral groove 14 to face the operating chambers (not shown). Number of 20 release channels • Of course, the area of each release channel is the same. The structure of the release path 20 can also be effectively reduced (for the first reading of the back, and then fill in this page) " m -I—-I ml. ，-0 ^ -7 This paper recognizes the standard i4 ; f! Chinese Sg house mark (rNS) (210X 297 mm) -15-40 (3 65 ABl V. Description of the invention (13) Compression and even the pressure of the liquid compression can also be applied to the closed container in Figure 6 Inside 50 • Closed 5 2 • The above-mentioned compression mechanism unit 5 1 is provided with a roller piston (hereinafter referred to as the above-mentioned roller 5 4), both ends of which are pivoted into a pivot support hole portion fixed in the closed container 50, and the pivot support is enabled. Cylinder 5 3 On the other hand, the ends of the shaft of the shaft portion of the shaft are compressed at the end of the cylinder, and the main ends of the shaft can be rotated 屮 4 \ i3 J f f ·, AH is printed with a metal main bearing 5 5, Only the rotation from the roller 5 4 to 5 3 is referred to here as the first cylinder bearing 5 8 is used only in the No. G path with the discharge port 6 5 · 1st, annular * the above along the axis side 5 between the formed and countershaft cylinder • Forced transmission The cylinder shaft located in the figure is called 2 cylinder, and the cylinder bearing 5 6 3 on the G side of the discharge path is provided to the right side of the drum . The position is the second bearing 5 passage, and the sealed bearing 5 7 is eccentric between the outer periphery and the rotation force transmission 5 4. The main bearing is provided on the left cylinder bearing 8 in the figure, so it is called the container 5 0. The rotary vane mechanism is on the cylinder 5 4 · 5 4a. The bearing 5 is free. · On the inner diameter, 5 8 • Above. 1 and the motor part 5 3, the eccentric fitting, 5 4 b is inserted into 5 and the auxiliary bearing 5 6, which are respectively press-fitted and inserted between the shaft center of the drum 5 4 and the cylinders 5 3 and 6 6 so that Cylinder second cylinder bearings 57 and 5 discharge passage G. In the second steam direction, a pair of gas and gas passages G are provided on the side of the cylinder bearing 5 7 on the side of the cylinder bearing 5 7 and on the side of the sub bearing 5 6. This gas passage and discharge path • Furthermore, a discharge pipe 8 is provided on the peripheral wall provided, and a thick part of the cylinder bearing 5 8 is formed, and the axis symmetrical position of the cylinder bearing 1 ^ --- M ---- I # ------ Order ------- line. (&Quot; Please read the precautions for the back and then " «? This page) This paper refers to the state ^ prisoner's standard (ns's) } 8 4 old cases (210X297 mm) -16-A7 ___ 406165 B7____ V. The hole in the description of the invention (14) · The suction container 5 9 is connected to one side of the sealed container 50, and the suction A guide passage 60 is provided in the main bearing 55. The guide suction passage 60 is provided from one end surface of the roller shaft portion 5 4a in the direction of this axis and further communicates with the roller shaft portions 54a and 54b. Suction passages 6 opened in the outer peripheral surfaces of the end portions of the roller bodies 5 4 c between each other. · A spiral groove 6 2 is formed in the peripheral surface of the roller body 5 4 c with a gradually decreasing pitch from one end side to the other end side. * In this groove, the spiral blades 63 are freely inserted in and out. Therefore, the space between the inner peripheral surface of the cylinder 53 and the peripheral surface of the roller 54 is divided by the blades 63. A plurality of operating chambers 6 4 ... which are gradually reduced in volume from one end side to the other end side of these spaces, that is, from the suction part A side to the discharge part B side. On the side wall surface of the discharge portion B of the spiral groove 62, a release passage 2 0A having the same configuration as the release passage 20 of the vane compressor described above is provided. However, each release passage 20 A is here. The screw position angle is specified to be 360 ° or less. · With the compressor configured in this way, the rotary cylinder 5 3 * is transmitted to the drum 54 via the rotary transmission mechanism 6 6 when the motor 5 2 is energized. * The cylinder 53 and roller 54 rotate synchronously at relative peripheral speeds while maintaining the original positional relationship due to the different radii from each other. With the rotation of cylinder 5 3 and roller 5 4, the blade 6 3 is relative to the spiral paper size. Luzhou Central SS Family Logo (CNS) Λ4ί ^ (210 X297 ^ «·) ~ ~ I J --- M ----.------ Order ------- line · (" (Read the precautions on the back first and then reappear on this page) Attachment 1 No. 86107428 Patent Application Chinese Manual Correction Page A7 B7 October, Republic of China Rev. 5. Description of invention (members are kindly requested to make clear; \ ': the original substance printed by the Intellectual Property Bureau of the Ministry of Economic Affairs and the Consumer Cooperatives printed 15 spiral grooves 6 2 in and out, protruding / submerged in the direction of the diameter of the drum. Therefore, the refrigerant gas is drawn from The tube 59 is sucked through a guide path 60 ′ formed in the main bearing 55 and the suction path provided in the drum 54 is guided into the cylinder 5 3 β and 'is sucked into the cylinder 5 · * 3. The refrigerant gas is sequentially transferred from the operation chamber 64 located on the suction side A side among the operation chambers 64 to the operation chamber 64 located on the discharge side B side. Further, when the refrigerant gas is sequentially transferred between the operating chambers 64, it is gradually compressed. When it is transferred to the last operating chamber on the side of the discharge portion B, it is raised to a predetermined pressure, and guided therefrom along the discharge path G of the second cylinder bearing 58. Then, the high-pressure body is discharged from the discharge path G into the closed container 5 ◦. Once the container is filled, the high-pressure body is guided to the discharge pipe 6 5 and is led to an external refrigeration cycle machine. With this type of screw vane compressor, when an over-compression state is established as the operating chamber 64, a release passage 2 OA provided on the B side of the discharge portion of the operating chamber is guided from a high-pressure gas when it is opened from the vane 63. Therefore, the high-pressure gas is sequentially guided from the actuating chamber 64 to the actuating chamber 64 on the discharge section B side through each release path 2 OA, and finally the last actuating chamber from the ejection part B side is formed through the ejection path G. It is guided into the hermetic container 50, and the pressure is quickly reduced to suppress the loss caused by over-compression, and it becomes a stable compression effect. FIG. 7 is based on the premise that the compression mechanism portion 51 of the spiral blade type described previously in FIG. 6 is provided, and the central portion of the cylinder 53A is used as a boundary. 1 B, saying that the paper size applies to the Chinese National Standard (CNS) A4 (210 x 297 mm) (please read the precautions on the back before writing this page) -Install -------- Order-- -------. 18 — 406: 65a7 ___ B7 V. Description of the invention (16) is a so-called paired compressor. (Furthermore, since this compressor is the compressor illustrated in Figure 6 Since it is a basic structure, the detailed description of the structure and function is omitted here.--A release passage 20B is provided on the wall surface on the side of the discharge portion B of each operating chamber 64, that is, the compression mechanism portion 5 of each system 1A, 5 1B, with release paths 20B in phase with each other · The compression mechanism sections 5 1A, 5 1B of each system, have the effects formed by the above-mentioned release path 2 〇 B. The results are the same as the previous Figure 1 and 6 The screw vane compressor illustrated in the figure is exactly the same. In addition, for a compressor provided with such paired compression mechanism sections 5 1 A and 5 1 B, the above-mentioned release passages 2 0 B are provided at the same phase positions of the two compression mechanism sections. When the mechanism system reaches the same pressure • High-pressure descent begins at the same time. Therefore, during the compression process of the 5 1 A and 5 1 B systems of the two compression mechanisms, there is no uneven pressure and stable compression performance can be obtained. • Also, because there is no pressure imbalance, the roller 5 4 A will not move in the thrust direction of either side, and it will not collide with other parts such as bearings to generate noise. As shown in FIG. 8, the depth L of the release path 20 C (that is, the size from the circumferential surface of the roller 11 to the bottom surface of the release path) is set to a depth that is 1 to 4 spiral grooves (that is, from the roller 1). The dimension from the circumferential surface of 1 to the bottom of the spiral groove is shallow (L <D). Under normal compression, gas is prevented from leaking from the bottom surface of the spiral groove 14 to the adjacent working chamber through the release passage 2 0 C. This percentage is described in terms of mt (CNS) / \ 4 ^ m (210X297 / ^^) I --- M ---- I · " ------ Order ------ Silver. -(ii read the previous note and note ¾ matters again on this page) A7 B7 printed by the Consumer Cooperatives of the Intellectual Property Bureau of the Ministry of Economic Affairs V. Description of the invention (17) As shown in Figure 9 • The channel 2 0D will be released When the width (diameter) is set to X and the diameter of the bottom of the spiral groove 14 is set to 4 d 0 • Set to establish a relationship of XS0.6d0 •: In addition, a tool (cutter) is actually made to release the passage 2 〇 E) 6 5. Use the tool that made the spiral groove 20D as it is. That is, • After cutting the circumferential surface of the roller 1 1 and setting the spiral groove 14, you can change to a cutting release channel without changing the tool. 2 0D · Therefore, the tool replacement procedure can be omitted. At the same time, there is no troublesome positioning caused by tool replacement. Moreover * The operating machinery described above are all equipped with screw blade compressors, but they are not limited to This * can also be applied to pumps with a spiral vane-type pump mechanism. [Effects of the invention] As described above, according to the invention of the first patent application, the release path is provided on the side wall surface of the spiral groove. When the operating chamber exceeds a predetermined pressure, this pressure is released to the operating chamber on the discharge side. Therefore, the excessive stress applied to the blades disappears, and the pressure can be reliably released from the operating chamber. The pressure loss achieves the effect of improving reliability. According to the invention in the scope of patent application No. 2, the release path faces the actuation chambers, and the actuation chambers from the suction side to the discharge side gradually expand the passage area. According to the invention in item 3 of the scope of patent application, the number of paths is gradually increased from the actuating chamber of the suction side to the discharge side. The paper size is applicable to the Chinese National Standard (CNS) A4 specification (210 × 297 mm) -20-m- ^ n nn Tten I 1 ^ 1 nJ nn Mm In mt m ^ r 1 · ϋ ^ ϋ 4 (Please read the notes on the back before filling this page)-· " " • Τ 屮 " J:! v- ^: u lv '-;,: fA ”: ;; :: .. A7 B7 Five' invention description (18) Therefore, according to the inventions in the scope of patent application No. 2 and No. 3, the action chamber is moved to the high-pressure side. The larger the area of the release path, the pressure can be reliably released for the over-compression or fluid compression generated early in the compression process. According to item 4 of the scope of patent application, the depth of the release path is formed to be larger than the spiral groove. The depth is relatively shallow, and it can reliably prevent leakage from the bottom of the spiral groove of the adjacent operating chamber during the compression process in the normal state. According to item 5 of the scope of patent application, the operating mechanism is set with the central part of the cylinder as a boundary. Left and right in pairs, because the release path is The counter-actuating mechanism achieves the same pressure in the same phase, so there is no pressure imbalance between the two actuating mechanism systems, and stable compression performance can be obtained. [Simplified description of the drawing] Figure 1 shows A longitudinal sectional side view of a spiral vane compressor of a fluid machine according to an embodiment of the present invention. Fig. 2 is a perspective view of a roller having blades wound in a spiral groove in the same embodiment. Fig. 3 (A) shows An explanatory diagram of the relationship between the blade and the spiral groove in the normal compression process of the same embodiment. ≫, Fig. 3 (B) is an explanatory diagram in an over-compressed state, and Fig. 4 is a roller of another embodiment. Partial perspective view. Fig. 5 is a partial perspective view of a roller of another embodiment. Fig. 6 is a longitudinal paper thick scale ii of a spiral vane compressor of another embodiment; n (('NS) Λ4 ^ (210X 297 ^ *) ~ -21-(诮 Please read the first note, please fill in the note 4 below ,; wood page) ¾ TJ '-β A7 B7 406165 V. Description of the invention (19) Sectional side view * The 7th circle is the other Of the spiral vane compressor of the present embodiment Side view · Figure 8 is a partial three-dimensional circle of a roller of another embodiment · Figure 9 is a partial three-dimensional view of a roller of another embodiment · Figures 10 (A) (B) show general compression Diagram of stroke and over-compression state. [Illustration of drawing number] 5, 50: Cylinder 11, 54, 54A: Drum 14, 62: Screw mechanism 1 6, 6 4: Actuating chamber 1, 5, 6 3: Blade 3, 51 , 51A, 51B: Actuating mechanism units 20, 20A, 20B, 20C, 20D: Release path ί. -VI! ^^^ 1-· *-= nn In i nn 1-士-II li SI— 一 J ^^ , T (Please read the notes on the back before filling out this page) *. The paper size printed by the Consumer Cooperatives of the Intellectual Property Bureau of the Ministry of Economic Affairs applies to the Chinese National Standard (CNS) A4 specification (210 '乂 297 mm)