經濟部中央標準局員工消費合作社印製 i、發明説明（1 ) 明領域： 本發明通常係指離心壓縮機’並特別指一離心壓縮機可 變管路升麼器之傳動定位機構’及背隙調整機構。 習知枯嫌f背景 當使用離心蒸氣壓縮機於大範圍的壓縮負荷時，最主要 的問題之一為流體通過壓縮機時的穩定程度。壓縮機入 口 '葉輪與升壓器通道必須經過設計，以提供意欲之最大 組積流率。當一低體積流率通過此一壓縮機時，流體會變 的不穩定。一但體積流率從一穩定範園下降，部分些微不 穩定的流體會進入壓縮機中。在此範圍内，升壓器通道中 將出現部分逆流’並產生噪音及減低壓縮機效率。在此範 圍之下，壓縮機進入所謂的突擊波，於升壓器通道中產生 週期性完全逆流，破壞機器的效率，並危害機器元件的完 整性。既然在許多壓縮機用途上，希望—大範圍的體積流 率，自然也已有建議許多修正，以改進低體積流率下，流 體的穩定性。 許多技術已經設計成能夠在大的操作範圍中，維持高機 器效率。在美國專利號碼4,378,194中，整個升壓器輪廊 可依負荷的改變而不同，使機器性能配合變化的負荷需 求。可調整升壓限流器亦描述於美國專利號碼3 362 625 中，可調節升壓器中之流體，以改進低體積流率下，流體 的穩定性》 在離心壓縮機中，一種在大流率範園維持高操作效率之 常見技術’為透過與固定升壓器導葉連接之可變寬度升壓 -4- 本紙張尺度適用中國國家樣準（CNS>A4規格（210X297公釐） nn In nn m ·IJ-,C^ f^K ^^^1 l a (請先閲讀背面之注意事項再填寫本頁) 訂 線 經濟部中央標準局員工消費合作社印«. 五、發明説明（2 ) 器的使用》 屬同一委託者之美國專利號碼2 996 996與4 378 194 中，描述可變寬度葉片升壓器，其中升壓器葉片固定地附 著至升壓器壁之一，如利用螺栓。葉片適於通過另一壁上 之開口，如此，允許升壓器的幾何形狀隨著負荷狀況而改 變。 固定地安裝升壓器葉片至升壓器壁之一，顯示許多問 題，特別是關於機器的製造、維修與操作。在總成中，僅 有少量空間夠於固定葉片。當葉片重新歸位時，任何葉片 的失準都將引起葉片糾結或摩擦對壁。同樣地假使總成 中-個或多個串接的葉片必須更換，則大致上整個機器必 須予以拆解，以便於更換。 壓縮機的效率可藉由變化升壓器的出口幾何形狀而大大 地強化。在一般性讓渡之美國專利申請序號〇8/6588〇ι 中，已揭露一種可變幾何形狀管路升壓器，並特此合併為 參考案。可變幾何形狀管路升壓器（亦可稱為分環管路升壓 器)將升壓器分成-第-内環與一第二外環。内環與外環間 具有互補入流通道區。意即每一個内環之入流通道區，在 外環中會對應一互補之入流通道區。內 κ 内衩與外環可個別互 相旋轉’藉由改變全開位置與部分關閉 Π刀關閉位置間之壓力範圍 來改進效率。在部分關閉位置，升愚器出口管的失準會增 加澡音。若環的旋轉並非最佳料點，料成額外的^ 音’並減低效率。 離心壓縮機内之幾何公差相當小。同择 ^ , 同時’壓縮機内的負 ---裝----rrITJ------線 (請先閱讀背面之注意事項再填寫本頁) -5 經濟部中央標準局貝工消费合作社印製 _Β2____ 五、發明説明（3 ) 荷貝丨相4大，且天生具有動態的特性。在一分環管路升磨 器中，維持動態負荷表面公差的問題，變得相當繁重。在 這對環上，軸向負荷（推力）或圓周上的負荷皆需被考慮。 升壓環必須能夠彼此相互旋轉，並且同時在相對位置上， 必須能維持嚴密的控制，以確保流體通道及壓縮機最終效 率能適當地配合。在一分環升壓器中，維持所需的公差， 大致上必須付出非常高的成本。 分環升壓器的另一個問題，為工件過早磨損。大致上無 法運用於離心壓縮機之氣流區，以排除氣體的污染。因流 出葉輪之氣流，而加諸於分環升壓器上之動態負荷，在無 潤滑油的情況下’會磨損加速中的升壓器元件。 能夠正確地將環彼此定位的傳動系統，在所有條件當 中’最重要的是必須具有足夠的剛性，以避免元件任何的 磨損。因為圓環圓周上的負荷，内環有相對外環震盪的傾 向，引起壓縮機不穩定與工件磨損，並且不利操作效率， 因而導致數個必須被克服的難題。因此，需要一種能夠防 止内壤與外環間相對運動的傳動系統，亦需要一種軸承的 觀念’允許雙環間相對的旋轉，並且能夠在維持雙環間嚴 密幾何公差的同時，忍受圓周與推力負荷。同時，亦需要 提供一種疋位系統，包括正確的最小與最大止樓，以避免 不需要的噪音與效率減衰，以及包括簡單的現場修正。此 外’傳動與轴承系統需要具有長操作壽命，及易於安裝與 適當調整等特性。 發明概诚 -6 · 本紙張尺度適用中國國家標嗥（CNS )六4現格（2丨〇χ297公釐） ---^--LI--< 貧裝—I--1 r—irL------取 (請先閲讀背面之，江意事項存填寫本頁) A7 B7 五、發明説明（4 =據其主要的觀點與廣泛地描述，本發明係指—離 ，’ ·又可變幾何形狀管路升壓器，更特別指用於— 縮可變幾何形狀管路升壓器中之傳動定關 之背隙調整機構。 偁興相關 一齒條接著於本發明，一可變管路升壓器之内環。— 齒輪則接著於固定至―離心壓縮機外殼之 ，齒條鳴合排列。旋轉傳動機構料壓器管部 /刀關閉〈位置間’可旋轉内環相對於外環運動。此外，傳 動=構能夠在全開與部分關閉間之眾多位置，對準升壓器 之管路。一行程限制器亦可正確地限制内環的行程於全開 與部分關閉之位置。背隙調整機構具有—與第—中心線同 心之外罩，及一通過其中並與第二中心線同心之内孔 ㈣固^於-通過内孔之傳動軸。外罩則可旋轉地固定至 外殼。本發明之外罩可對第二中心線旋轉操作，以調整齒 條與小齒輪間之背隙。 附圖餘诚 在附圖中，號碼用來指示整個視圖中相同的元件； 圖1為依據本發明，壓縮機之斷面側视圖，具有一可變 管路升壓器； Λ 經濟部中央樣準局貝工消費合作杜印製 圖2為依據本發明，一可變管路升壓器之透視圖； 圖3與4為依據本發明，-可變管路升壓器之斷面前視 圖’個別於一第一全開與第二部分關閉位置. 圖5為一壓縮機之上視圖，具有本發明之可變管路升壓 器； 本紙張尺度適用中國國家標準（CNS ) Α4規格（210X297公釐） -------- 五、發明説明（ 。圖6為本發明中，大致上沿圖5之剖面線6_6選取，一 圓環支撐機構之斷面視圖； 圖7為本發明中，大致上沿圖6之剖面線7·7選取，一 圓環支撐機構之斷面視圖； 圖8為本發明中，一滾子總成之斷面視圖； 圖9為本發明中，一軸之斷面视圖； 圖10為本發明圖1之詳細區域10中，一定位像動機構 之斷面視圖； 圖11為本發明中，一定位傳動機構之上視圖； 圖12為本發明中，一齒條之透视圖； 圖13為依據本發明，一可變管路升壓器之性能圖； 圖1 4為一僅具有入口導葉之壓縮機之性能圖； 圖15為依據本發明，具有一可變管路升壓器與入口導葉 之壓縮機之性能圖；與 圖1 6為依據本發明，具有一抽向限制機構之壓縮機之斷 面视圖。 主要元件代表符號 ---- - -----裝-----；--«—訂 -------線 (請先閲讀背面之注意事項再填寫本頁) 經濟部中央標準局貝工消費合作社印裝 10 離心壓縮機 12 葉輪 14 升壓器 16 收集器 19 高速抽 23 壓縮吸入區 29 入口開口 -8-Printed by the Employees' Cooperative of the Central Standards Bureau of the Ministry of Economic Affairs i. Description of the invention (1) Field of the invention: The present invention generally refers to a centrifugal compressor 'and in particular a transmission positioning mechanism of a centrifugal compressor variable pipeline lifter' and the back Gap adjustment mechanism. BACKGROUND OF THE INVENTION When using centrifugal vapor compressors in a wide range of compression loads, one of the most important issues is the degree of stability of the fluid as it passes through the compressor. Compressor inlet 'impeller and booster passages must be designed to provide the desired maximum accumulation rate. When a low volume flow rate passes through the compressor, the fluid becomes unstable. Once the volume flow rate drops from a stable range, some slightly unstable fluid will enter the compressor. Within this range, there will be some backflow 'in the booster channel, which will generate noise and reduce compressor efficiency. Under this range, the compressor enters the so-called assault wave, which generates a periodic complete backflow in the booster channel, destroying the efficiency of the machine and endangering the integrity of the machine components. Since for many compressor applications, a wide range of volume flow rates is desired, many modifications have naturally been suggested to improve the stability of the fluid at low volume flow rates. Many technologies have been designed to maintain high machine efficiency over a wide operating range. In U.S. Patent No. 4,378,194, the entire booster wheel gallery can be varied based on changes in load to match machine performance to changing load requirements. Adjustable boost restrictor is also described in U.S. Patent No. 3 362 625. The fluid in the booster can be adjusted to improve fluid stability at low volume flow rates. In centrifugal compressors, A common technique for maintaining high operating efficiency of the lifanyuan 'is a variable width boost through a fixed booster guide vane. -4- This paper size is applicable to China's national standard (CNS > A4 size (210X297mm) nn In nn m · IJ-, C ^ f ^ K ^^^ 1 la (Please read the precautions on the back before filling out this page) Printed by the Consumers' Cooperatives of the Central Standards Bureau of the Ministry of Economic Affairs. V. Description of the Invention (2) "Usage", US Patent Nos. 2 996 996 and 4 378 194, belonging to the same client, describe variable width blade boosters in which the booster blades are fixedly attached to one of the booster walls, such as using bolts. Blades Suitable to pass through an opening in the other wall, thus allowing the geometry of the booster to change with load conditions. The fixed installation of the booster blades to one of the booster walls reveals many problems, especially regarding the machine Manufacturing, maintenance and operation. In the process, there is only a small amount of space to fix the blades. When the blades return to their original position, any misalignment of the blades will cause the blades to tangle or rub against the wall. Similarly, if one or more blades in series in the assembly must be Replacement, generally the entire machine must be disassembled to facilitate replacement. The efficiency of the compressor can be greatly enhanced by changing the outlet geometry of the booster. US patent application serial number 08/6588, which is generally assigned. 〇ι, a variable geometry pipeline booster has been disclosed, and hereby incorporated into a reference case. The variable geometry pipeline booster (also known as a split loop pipeline booster) Divided into-the first inner ring and a second outer ring. There is a complementary inflow channel area between the inner ring and the outer ring. This means that the inflow channel area of each inner ring will correspond to a complementary inflow channel area in the outer ring. κ The inner ring and the outer ring can rotate with each other individually to improve the efficiency by changing the pressure range between the fully open position and the partially closed Π knife closed position. In the partially closed position, the misalignment of the exit tube of the lifting device will increase the bath sound. Rotation of the ring and The best material point, the material becomes extra ^ sound 'and reduces the efficiency. The geometric tolerance in the centrifugal compressor is quite small. With the same choice ^, at the same time,' negative in the compressor ------------------- ITJ -------- (Please read the notes on the back before filling out this page) -5 Printed by the Shellfish Consumer Cooperative of the Central Standards Bureau of the Ministry of Economic Affairs _Β2 ____ V. Description of the Invention (3) The Hubei has four major phases and is inherently dynamic. The problem of maintaining dynamic load surface tolerances in a split loop pipe lifter becomes quite onerous. On this pair of rings, axial load (thrust) or load on the circumference must be considered. The booster ring must They must be able to rotate with each other, and at the same time in relative positions, they must maintain tight control to ensure that the fluid channels and the compressor's final efficiency can be properly matched. In a split-loop booster, maintaining the required tolerances generally requires a very high cost. Another problem with split ring boosters is premature wear of the workpiece. Generally, it cannot be used in the air flow area of centrifugal compressors to exclude gas pollution. Due to the airflow flowing out of the impeller, the dynamic load imposed on the split-ring booster will wear out the booster element during acceleration without lubricant. A drive system capable of correctly positioning the rings with each other must, among all conditions, be sufficiently rigid to avoid any wear of the components. Due to the load on the circumference of the ring, the inner ring has a tendency to oscillate relative to the outer ring, which causes instability of the compressor and wear of the workpiece, and adversely affects the operating efficiency, resulting in several problems that must be overcome. Therefore, there is a need for a transmission system that can prevent the relative movement between the inner soil and the outer ring, as well as the concept of a bearing 'to allow relative rotation between the two rings, and to endure the circumference and thrust load while maintaining the tight geometric tolerances between the two rings. At the same time, it is also necessary to provide a niches system, including the correct minimum and maximum stops, to avoid unwanted noise and efficiency attenuation, and include simple field corrections. In addition, transmission and bearing systems need to have long operating life, as well as ease of installation and proper adjustment. Sincere invention -6 · This paper size is applicable to China National Standards (CNS) June 4 and 4 (2 丨 〇χ297mm) --- ^-LI-< Poor-fitting--I--1 r-irL ------ Take (please read the back page first, Jiang Yi matters deposit and fill out this page) A7 B7 V. Description of the invention (4 = According to its main point of view and extensive description, the present invention refers to-from, '· The variable geometry pipeline booster is more specifically referred to as a backlash adjustment mechanism for the fixed closing of the transmission in the variable geometry pipeline booster. A rack related to the present invention follows, The inner ring of the variable line booster. — The gear is then fixed to the “centrifugal compressor casing, and the racks are arranged in a ring. The rotary drive mechanism pressure tube / knife closed <position 'can be rotated inner ring Relative to the outer ring movement. In addition, the transmission = structure can align the pipeline of the booster in many positions between fully open and partially closed. A stroke limiter can also correctly limit the stroke of the inner ring between fully open and partially closed Position. The backlash adjusting mechanism has a -concentric outer cover with the first center line, and one passing through it and the second center line The inner hole of the heart is fixed to the transmission shaft through the inner hole. The outer cover is rotatably fixed to the outer shell. The outer cover of the present invention can be rotated to the second centerline to adjust the backlash between the rack and the pinion. Drawings Yu Cheng In the drawings, numbers are used to indicate the same elements throughout the view; Figure 1 is a sectional side view of a compressor according to the present invention, with a variable line booster; Λ Central of the Ministry of Economic Affairs Figure 2 is a perspective view of a variable pipeline booster according to the present invention; Figures 3 and 4 are broken front views of a variable pipeline booster according to the present invention. 'Individually in a first fully open and second partially closed position. Figure 5 is a top view of a compressor with the variable line booster of the present invention; this paper size applies to China National Standard (CNS) Α4 specifications (210X297 (Mm) -------- 5. Description of the invention (. Fig. 6 is a cross-sectional view of a ring-shaped support mechanism in the present invention, which is roughly selected along the section line 6_6 of Fig. 5; Fig. 7 is the present invention Medium, selected roughly along the section line 7 · 7 of Fig. 6, a cross-sectional view of a ring support mechanism FIG. 8 is a cross-sectional view of a roller assembly in the present invention; FIG. 9 is a cross-sectional view of a shaft in the present invention; FIG. 10 is a detailed image of a positioning mechanism in FIG. Sectional view; Figure 11 is a top view of a positioning transmission mechanism in the present invention; Figure 12 is a perspective view of a rack in the present invention; Figure 13 is a performance diagram of a variable line booster according to the present invention Figure 14 is a performance chart of a compressor with only inlet guide vanes; Figure 15 is a performance chart of a compressor with a variable line booster and inlet guide vanes according to the present invention; and Figure 16 is According to the present invention, a cross-sectional view of a compressor having a pumping direction restricting mechanism. The main components represent symbols ---------- installation -----;-«-order ----- --- line (please read the precautions on the back before filling this page) Printed by the Central Standards Bureau of the Ministry of Economic Affairs, Shelley Consumer Cooperatives 10 Centrifugal compressor 12 Impeller 14 Booster 16 Collector 19 High-speed pumping 23 Compression suction area 29 Inlet opening -8-
本紙張尺度賴巾關家紗（CNS >Α4· (210x297公D 經濟部中央標準局員工消費合作社印製 Λ八 Α7 ^〇2β6〇_β7_ 五、發明説明（6 ) 31 吸入外罩 32 葉片環總成 33 導葉 34 外罩 35 圓環支撐機構 36 滚軸總成 37 軸 38 六角頭 39 軸螺栓 40 内環 41 内軸承插槽 42 外環 43 缺口 44 流體通道區 45 外軸承插槽 46 流體通道區 47 軸體 48 軸體中心線 49 軸内孔 50 軸内孔中心線 52 流體通道 53 内環4 0與外環4 2間之接面寬度 54 滾子總成 55 滾子 -9- 本紙張尺度適用中國國家標準（CNS ) Α4規格（210Χ297公釐） „---^----%,, ·裝-----—.丨訂^------線 (請先閱讀背面之注意事項再填寫本頁) 經濟部中央標準局員工消費合作社印製 4〇26ββ 五、發明説明（7 ) 56 外袖承面 57 推力轴承面 58 固定孔 59 螺孔 60 性能曲線 62 性能曲線 64 性能曲線 66 性能曲線 68 性能曲線 70 顫動點 72 顫動點 73 凸肩 74 凸肩 80 曲線 81 轉折點 82 曲線 84 曲線 86 曲線 88 曲線 90 軸向限制系統 91 螺紋主軸 92 螺紋固定孔 93 軸承板 94 閉鎖螺帽 „ „----'•I -裝-----—.I 訂^------..線 (請先閱讀背面之注意事項再填寫本頁) 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） A7 A7 經濟部中央標隼局員工消費合作社印裝 ^0^6ββ- 五、發明説明（8 ) 95 六角頭 96 凹口 101 性能曲線 102 性能曲線 103 性能曲線 104 性能曲線 105 性能曲線 111 性能曲線 112 性能曲線 113 性能曲線 114 性能曲線 115 性能曲線 116 性能曲線 121 定位傳動機構 123 齒條 124 小齒輪 125 軸外罩外表面 126 小齒輪軸 127 外罩中心線 128 啟動器 129 外罩内孔 130 包覆外罩 131 外罩内孔中心線 132 壓縮機内面 -11 - ---_---^----νί.裝-----—.—訂^------線 (請先閱讀背面之注意事項再填寫本頁) 本紙張尺度適用中國國家標準（CNS ) Α4規格（210X297公釐） 經濟部中央標準局員工消費合作社印装 402666五、發明説明（9 133 有頭螺釘 134 §周整插槽 135 扳手平板 137 腔 138 螺孔 139内環40之凸部 140腔137之全開止樓 141腔137之部份打開止樓 142 齒輪固定孔 143 圓環形凹槽 144 齒面 145 齒面 Κ·2 葉輪尖的半徑 R3 内環4 0之外半徑 R4 外環4 2之外半徑 Τ 内環厚度 較佳實例之評細說明 參照圖1 ’本發明安裝於一離心壓縮機1 〇中，成為 H VAC系統（未顯示）之一部份，此系統具有—葉輪丨2以加 速冷卻劑蒸氣至高速，一升壓器1 4於動能轉變至壓力能 時’減低冷卻劑至低速，以及一以收集器1 6形式存在之 排放室’以收集隨後流至一濃縮器之流體所排放之蒸氣。 葉輪1 2之功率由一電動馬達提供，此電動馬達系w 封於壓縮機之另一端’並且可操作旋轉—高速軸19 ° -12- A7 B7 (請先閱讀背面之注意事項再填寫本頁) 裝· 1.1訂 線 本紙張尺度適用中國國家標準（CNS ) A4規格（210X297公釐） 經濟部中央標準局員工消费合作社印装 402663 五、發明説明（10) 接下來再參照冷卻劑流體在壓縮機10中所發生的行為。 冷卻劑進入吸入外罩3丨之入口開口 29，通過葉片環總成 32與導葉33，並且再進入壓縮吸入區23 ,此壓縮吸入區 形成壓縮區，其内邊由葉輪丨2所定義，其外邊由外罩34 所疋義。壓縮之後’冷卻劑流進升壓器1 4、收集器16與 排放管線中（未顯示）。 依據本發明’ 一可變幾何形狀管路升壓器14包括一第一 内環40與一第二外環42，一圓環支撐機構35與一定位 傳動機構121。參照圖3與4，内外環具有形成其中之互 補流體通道區4 4與4 6。意即内環4 0之每一流體通道區 44 ’具有一形成於外環42之互補通道區46。内環4〇與 外環4 2可互相旋轉。在一較佳實例中，内環4 〇在一靜止 外環42之圓周内旋轉。 如圖3與4所示，當一壤相對於另一環旋轉時，内環與 外環之每一對互補入流通道之對準會改變。環4〇與42於 圖3所示之第一全開位置與圖4所示之第二部分關閉位置 間為可調，其中在全開位置，互補通道區對準，並且最大 量的流體通過内外環4 0與4 2，在部份關閉位置，互補通 道失準’因此而限制了通過通道區4 4與4 6之流體。 依據本發明之一較佳實例’圖5顯示一圓環支撐機構 3 5。實例中圖解三個此類機構，分別位於等分升壓器圓周 之位置上。參照圖6 - 7 ’本發明之圓環支撐機構包括一内 轴承插槽4 1與一位於内環40中之缺口 43，一滾子總成 5 4，一滾軸總成3 6，與一位於外環中之外軸承插槽4 5。 -13- 本紙張尺度適用中國國家標準（CNS ) A4現格（210X297公釐） 走·裝-----—.I訂^------k (請先閱讀背面之注意事項再填寫本頁)This paper size Lai Jin Guan Jiasha (CNS > A4 · (210x297) D Printed by the Consumers' Cooperative of the Central Standards Bureau of the Ministry of Economic Affairs Λ 八 Α7 ^ 〇2β6〇_β7_ V. Description of the invention (6) 31 Inhalation cover 32 Blade ring Assembly 33 Guide vane 34 Cover 35 Ring support mechanism 36 Roller assembly 37 Shaft 38 Hex head 39 Shaft bolt 40 Inner ring 41 Inner bearing slot 42 Outer ring 43 Notch 44 Fluid passage area 45 Outer bearing slot 46 Fluid passage Zone 47 Shaft body 48 Shaft body center line 49 Shaft inner hole 50 Shaft inner hole center line 52 Fluid passage 53 Inner ring 4 0 and outer ring 4 2 Interface width 54 Roller assembly 55 Roller-9- This paper The standard is applicable to the Chinese National Standard (CNS) Α4 specification (210 × 297 mm) „--- ^ ----% ,, · Installation -------. 丨 Order ^ ------ line (Please read first Note on the back, please fill in this page again) Printed by the Consumer Cooperatives of the Central Standards Bureau of the Ministry of Economic Affairs 4026ββ V. Description of the invention (7) 56 Outer sleeve bearing surface 57 Thrust bearing surface 58 Fixing hole 59 Screw hole 60 Performance curve 62 Performance curve 64 performance curve 66 performance curve 68 performance curve 70 flutter point 72 flutter point 73 shoulder 74 Shoulder 80 Curve 81 Turning point 82 Curve 84 Curve 86 Curve 88 Curve 90 Axial restraint system 91 Threaded spindle 92 Threaded fixing hole 93 Bearing plate 94 Locking nut „… .I order ^ ------ .. line (please read the notes on the back before filling this page) This paper size is applicable to China National Standard (CNS) A4 specification (210X297 mm) A7 A7 Central Standard of the Ministry of Economic Affairs Printed by the Bureau ’s consumer cooperative ^ 0 ^ 6ββ- V. Description of the invention (8) 95 Hexagonal head 96 Notch 101 Performance curve 102 Performance curve 103 Performance curve 104 Performance curve 105 Performance curve 111 Performance curve 112 Performance curve 113 Performance curve 114 Performance Curve 115 Performance curve 116 Performance curve 121 Positioning transmission mechanism 123 Rack 124 Pinion gear 125 Shaft cover outer surface 126 Pinion shaft 127 Cover center line 128 Starter 129 Cover hole 130 Cover cover 131 Cover hole center line 132 In the compressor -11----_--- ^ ---- νί.Packing -------.-- Order ^ ------ line (Please read the precautions on the back before filling this page) This Paper size applicable National Standard (CNS) Α4 specification (210X297 mm) Printed by the Consumer Cooperatives of the Central Standards Bureau of the Ministry of Economic Affairs 402666. 5. Description of the invention (9 133 Cap screws 134 § Slots 135 Wrench plate 137 Cavity 138 Screw holes 139 Inner ring Convex part of 40. 140 cavity. 137. Full open stop building. 141 Part of cavity 137 open stop building. 142 Gear fixing hole. 143 Circular groove. 144 Tooth surface. 145 Tooth surface. K2. Radius of impeller tip. Radius R4 Outer ring 4 2 Outer radius T Inner ring thickness is better explained with reference to Figure 1 'The present invention is installed in a centrifugal compressor 10 and becomes part of an H VAC system (not shown). The system has-an impeller 丨 2 to accelerate the coolant vapor to high speed, a booster 14 to 'reduce the coolant to low speed when the kinetic energy is converted to pressure energy, and an exhaust chamber in the form of a collector 16' to collect the subsequent Vapor discharged from a fluid flowing to a concentrator. The power of the impeller 12 is provided by an electric motor, which is sealed at the other end of the compressor 'and can be rotated-high speed shaft 19 ° -12- A7 B7 (Please read the precautions on the back before filling this page ) Installation 1.1 Binding This paper size applies Chinese National Standard (CNS) A4 specification (210X297 mm) Printed by the Consumer Cooperatives of the Central Standards Bureau of the Ministry of Economic Affairs 402663 V. Description of the invention (10) Next refer to the coolant fluid under compression Occurred in the machine 10. The coolant enters the inlet opening 29 of the suction cover 3, passes through the blade ring assembly 32 and the guide vane 33, and then enters the compression suction area 23. This compression suction area forms a compression area, and the inner side is defined by the impeller 2 and its The outer side is defined by the cover 34. After compression 'the coolant flows into the booster 14, the collector 16 and the discharge line (not shown). According to the present invention ', a variable geometry pipeline booster 14 includes a first inner ring 40 and a second outer ring 42, a ring support mechanism 35 and a positioning transmission mechanism 121. Referring to Figures 3 and 4, the inner and outer rings have complementary fluid channel regions 44 and 46 formed therein. That is, each fluid passage region 44 'of the inner ring 40 has a complementary passage region 46 formed in the outer ring 42. The inner ring 40 and the outer ring 42 can rotate with each other. In a preferred embodiment, the inner ring 40 rotates around the circumference of a stationary outer ring 42. As shown in Figures 3 and 4, when a soil rotates relative to another ring, the alignment of each pair of complementary inflow channels of the inner ring and the outer ring changes. Rings 40 and 42 are adjustable between the first fully open position shown in FIG. 3 and the second partially closed position shown in FIG. 4. In the fully open position, the complementary channel regions are aligned, and the maximum amount of fluid passes through the inner and outer rings. 40 and 42, in the partially closed position, the complementary channels are out of alignment, thus restricting the fluid passing through the channel zones 44 and 46. A preferred embodiment according to the present invention 'Fig. 5 shows a ring support mechanism 35. Three such mechanisms are illustrated in the example, and are located on the circumference of the equally divided booster. Referring to FIGS. 6-7 'The ring supporting mechanism of the present invention includes an inner bearing slot 41 and a notch 43 in the inner ring 40, a roller assembly 5 4 and a roller assembly 3 6 and a Located in the outer ring outside the bearing slot 4 5. -13- This paper size is applicable to Chinese National Standard (CNS) A4 now (210X297mm) Walk and install ----- .. I order ^ ------ k (Please read the precautions on the back before (Fill in this page)
1〇2& 五、發明説明（11 ^ 8所V，滾子職包括__具有_外n面 Γ3ΓΓ57之滾子。如圖6-7所示，滾轴總成包括」 =與-抽螺栓39。如圖9所示，37包括—六角頭 内孔中^趙Ο ’―袖體中心線48 ’―轴内孔49與一相 =中心線5〇。此外’抽螺栓39包括—對與轴内孔中心 線50同心之凸肩73、74。 法tit器：另—個問題，為工件過早磨損。大致上無 潤流’而加諸於分環升壓器上之動態負荷，在無 ’s /兄下，會磨損加速中的升壓器元件。由於在大 縮機中無潤滑油，因此大致上須採取—些措施來減 +摩察與磨損。-致地，在本發明將描述於下之特定實例 ’元件接面常經硬覆膜處理’工件則由超高分子塑膠材 枓製造，圓環總成經預負荷’而且藉由定位傳動系統之齒 輪來消除背隙。 接下來，探討内環組裝及運動的情形。外環42相對靜止 ^ 卜罩並且二組圓壤支撐機構3 5，藉由固定滾子總 成54於外環之軸承插槽45，並將軸通過固定孔58與滚 子”’《成，且安裝軸螺检39通過軸，最後，輕輕地旋轉軸 螺栓39進入外環中之螺孔59，以此方式安裝於外環。内 衣4〇以内％圓周上之缺口 43，對準轴承插槽45與滾子 總成3 5，再如圖7所示，順時針旋轉内環以固定滾子總成 於軸承插槽41内，以此方式安裝於外環内。當内環安裝 於外環内時’藉由一扳手旋轉六角頭3 8來旋轉中心軸， 14- 本紙張尺度適用巾（CNS ) 44規格（2ωχ297公楚） --L---r---,ί.裝----1—訂^------k {請先閲讀背面之注意事項再填寫本頁) 經濟部中央標準局員工消费合作社印裝〇2 & V. Description of the invention (11 ^ 8V, rollers include __rollers with _outside n plane Γ3ΓΓ57. As shown in Figure 6-7, the roller assembly includes "= and-withdraw bolts 39. As shown in FIG. 9, 37 includes—in the hexagonal inner hole ^ 赵 Ο '― sleeve center line 48 ――shaft inner hole 49 and one phase = center line 50. In addition,' pull bolt 39 includes-pair with Concentric shoulders 73, 74 of the centerline of the inner hole of the shaft 50. Tit device: Another problem is the premature wear of the workpiece. There is almost no lubricating flow, and the dynamic load on the split booster is Without 's / brother, the booster components during acceleration will be worn. Because there is no lubricant in the shrinking machine, roughly some measures must be taken to reduce + friction and wear.-By the way, in the present invention, The specific example described below is that the component interface is often hard-coated. The workpiece is made of ultra-high polymer plastic material, the ring assembly is preloaded, and the backlash is eliminated by positioning the gears of the transmission system. Let ’s discuss the assembly and movement of the inner ring. The outer ring 42 is relatively stationary ^ The cover and two sets of round soil supporting mechanisms 35 are fixed by rolling The assembly 54 is in the bearing slot 45 of the outer ring, and passes the shaft through the fixing hole 58 and the roller "", and the shaft screw inspection 39 is passed through the shaft. Finally, the shaft bolt 39 is gently rotated into the outer ring. The screw hole 59 is mounted on the outer ring in this way. The gap 43 on the circumference within 40% of the underwear is aligned with the bearing slot 45 and the roller assembly 35. Then, as shown in FIG. 7, rotate the inner ring clockwise to The fixed roller assembly is installed in the bearing slot 41 and installed in the outer ring in this way. When the inner ring is installed in the outer ring, the central axis is rotated by rotating the hexagon head 3 8 with a wrench, 14- this paper size Applicable towels (CNS) 44 specifications (2ωχ297 public Chu) --L --- r ---, ί. Outfit ---- 1—Order ^ ------ k {Please read the precautions on the back first (Fill in this page) Printed by the Consumer Cooperatives of the Central Standards Bureau of the Ministry of Economic Affairs
請 先 閲 讀 背 面 % 事 項 再 填 % 本 頁 _1〇2Μα-__五、發明説明（13 A7 B7 經濟部中央標準局貝工消費合作杜印製 ==，可…固定於外環42,而轴承板亦不會 意外接觸内環。—但外罩34安裝，則旋轉螺紋主抽9】帶 動軸承板接觸内環。隨著軸承板適當地定位可 閉鎖螺帽94來旋緊或旋鬆此機構。在一較佳實例中軸 承板由超冑分子塑膠材料所製造。本發明之—實財，包 括六個此種抽向）：艮制機構，纟内環外圍圓周上相隔相等= 間。 圖1〇中，描述一在外環42之圓周上，旋轉内環40之 足位傳動機構121。内環4G已固定地接著於自内環4〇徑 向向外延伸之齒條123。在齒輪連動關係中，齒條接 著於小齒輪124，並經由小齒輪軸126，由一啟動器丨28驅 動。選擇與控制啟動器128，使内環4〇在—第—全開位置 與第二部分關閉位置，以及任何中間位置，相對外環42 運動。小齒輪# 126外覆-包覆外罩咖，自壓縮機内面 132密封小齒輪轴126，並且此包覆外罩13()亦防止壓縮機 1〇内之流體經由包覆外罩丨30外&。㈣升壓器内之冷卻 劑流體，而施加於内環上之切線方向與圓周方向負荷，會 引起内環在外環中傾向來回顫動。内環多餘的運動或顏動 會使齒123與小齒輪124磨損，並且亦引起其他工件磨 損。如同稍早所討論的，經由滚子總成預加負荷至内環， 可防止内環運動，以及在正常操作狀況下產生之顫動。假 使在異常狀況下，如操作於顫動狀態，則需 — L級機構來 防止内環的運動。本發明提供一傳動定位系統，利用軸包 覆外罩130，經由調整小齒輪與齒條間相對之中心位置， (請先閲讀背面之注意事項再填寫本頁) 裝· 訂 線 16 本紙張尺度適用中國國家標準（CNS ) A4规格（210X297公釐） A7 B7 五、發明説明（14 以防止扇形齒輪與小齒輪間背隙之方式限制内環反向的 運動與_動。袖外罩外表s 125與外罩中心線127同心， 而外罩内孔129則與外罩内孔中心線1 3丨同心。在本發明 < 一較佳實例中，外罩中心線丨27與外罩内孔丨29彼此偏 移〇·60英吋1>參照圖Η，顯示定位傳動機構之扳手平板 135與調整插槽134。在安裝定位傳動機構進入吸入外罩 31後’放置—扳手（未顯示）橫跨扳手板135,旋轉傳動定 位機構，移除齒條123與小齒輪124間之背隙。一但達到 最小背隙，則旋緊有頭螺釘133，以固定定位傳動機構。 一但背隙被消除，内環運動的趨勢則可直接地經由齒輪系 統，由啟動器所掌控。 流體通過升壓器丨4 一第二部分關閉位置，相對於全開位 置流率 < 流動，取決於升壓器在部份關閉位置，流體通道 <最小斷面積，對全開位置，流體通道（由互補通道區44 與4 6所定義）最小斷面積之比率。已知為 ''喉部面積〃之 最小流體通道面積，當升壓器丨4於全開位置時，大致上 取決於内環通道44之流體通道52之最小直徑，當升壓器 1 4於第二部分關閉位置時，則由内環4 〇與外環* 2間之 接面寬度5 3所控制。舉例來說，假使一升壓器在第二部 分關閉位置，具有一最小面積（喉部面積）丨/8平方英吋， 並且在全開位置，具有一最小面積（喉部面積）丨/4平方英 叶則流在部分關閉位置，通過升壓器之流體體積流 率，將為全開位置體積流率之5〇%。當升壓器14於—第 二部分關閉位置時，通過壓縮機丨〇之流率，大致上會是 I /1 ^ „--訂------線 (請先閲讀背面之注意事項再填寫本頁) 經濟部中央橾準局負工消費合作社印製 -17 經濟部中央標準局貝工消費合作社印裂 402666 五、發明説明（15) 全開位置時，通過壓縮機1 0之流體流率約丨0%至1 00。/〇。 在一第二部分關閉位置時（圖4)，至少為全開位置約 1 〇 %之流體體積，將流過升壓器1 4，以防止過度的熱力加 熱過程、噪音’以及壓縮機效率的降低。結果，兩圓環區 間相對旋轉的量，受限於需使一第二部分關閉位置有效之 旋轉量，也就是說，兩環不可調整至完全關閉其間流體的 流動°兩環間允許旋轉的角度，取決於全開位置兩環間意 欲之流動，以及在圓環區4 0與4 2中，入流通道區4 4、 46相對於圓環區40與42體積之數目與體積。 接著參照圖4’ R2定義至葉輪尖的半徑，R3定義内環 40之外半徑，與R4定義外環之外半徑。内環4〇之量 T = R3-R2定義流體通過的厚度，不可過大，以免阻塞通 過外環通道46流體之意欲部位（例如流體的5〇%)，通過 升壓器1 4之流體的流動可被有效地控制。在發生任何升 壓之前，内環相對外環的旋轉將減少升壓器喉部面積如 此可防止流體於升壓後加速^同樣地，内環厚度τ越小， 流體通過在部份關閉位置之升壓器之轉角就越小。以上所 提兩種效應，在部份負荷操作狀況下，都會改善壓縮機 效率。 . 參照圖5與1 2，顯示本發明之一實例，具有一機構可提 供内環對應一第一全開位置與第二部分關閉位置正確之定 位。腔137加工於外環42巾，可容納齒條123。齒條^ 以凸凹的方式精確地固定於内環4〇，其中齒條備有二 形凹槽143，適於接納内環4〇之凸部139。内環定位於= ---_---„----ί裝-----.丨訂^------级 (請先閲讀背面之注意事項再填寫本頁} -18- '^濟部中央標準局員工消费合作社印製 -^〇26G〇- 五、發明説明（16 ) 環中以決定全開位置，並且兩環彼此相對旋轉，直到流體 通道52完全地與外流體通道46對準。若兩環在此位置， 且圓環支撐機構亦如前述加以調整，則固定齒條至内環， 且齒面145與腔137之全開止檔14〇接觸。屆時，安裝螺 检（未顯示）通過齒輪固定孔142，並且緊定至内環中之螺 孔138。齒條與腔具有一尺寸，以提供管路升壓器一預先 決定心緊密度。舉例來說，在本發明之—較佳實例中，腔 137之尺寸為使得當齒面丨44與腔〗37之部份打開止擋 14 1接觸時，齒條角寬度與腔之角寬度的差達到丨開口 位置。此例中，齒條所需的行程為度，齒條角寬度為 35度，而對應的腔角寬度為45度。齒條在如此定位之 下，可利用一介於齒條與腔之間之承停止檔，在對應一全 開位置與部分關閉位置之點上，猜確地且可重複地定位兩 袞承停止&亦允許啟動器丨2 8的現場修護，而不需調整 内外環的位置 本發明的操作與使用，可藉由圖13加以了解。依據本發 明，圖13帛* —具有可冑管路升壓器之壓縮機之性能 圖圖1 3之性能圖包括眾多之性能曲線6 〇、6 2、6 4、 66與68，每一條對應一介於内外環區4〇與42間之不相 連位置。每一條性能曲線，例如6〇之特徵，為具有一顫 動點，例如70，該點代表可獲取之最大壓力。操作一壓縮 機於-流率或低於顫動點，可能將造成一顏動狀況，如本 發明背景部份中所討論。 為了圖解本發明，舉例來說，曲線60可能對應-第-全 ---：------w 裳----*~·— 訂^------線 (請先閱讀背面之注意事項再填寫本頁} -19- 經濟部中央榡準局員工消费合作社印褽 402666 五、發明説明（17) 開位置’曲線6 2可能對應一差全開位置2度之部分關閉 位置，曲線64可能對應一差全開位置4度之部分關閉位 置，曲線6 8可能對應一差全開位置8度之部分關閉位 置。 可知’調整圓環區4 0與4 2至一關閉位置，具有調整一 壓縮機性能曲線中，如70與72之顫動點至一較低流率的 效應。如此，藉由調整升壓器圓環40與42至—關閉位 置，可避免低流速需求期間之顫動狀況。 藉由比較圖13中，一具有可變升壓器之壓縮機之性能 圖，與圖14中，一僅具有可調入口導葉之壓縮機之性能 圖’有助於了解本發明。圖14中，曲線80、82、84愈 8 8 ’對應導葉3 3逐漸關閉之不連續位置。可知，關閉導 葉33如關閉升壓器圓環區40與42 一般，具有降低顏動 點流率的效用。如此，可藉由調整入口導葉3 3至—關閉 位置，來避免一顫動狀況。 然而’可從圖1 4之性能圖得知，調整導葉3 3至—關閉 位置’進一步具有在顫動點減低自壓縮機1 〇而來之壓力 頭之效應。因此，一需要較高壓力之低流率操作狀況，無 法單獨藉由調整導葉3 3加以滿足。 比較上’可從圖1 3之性能圖得知’在升壓器圓環4 〇與 4 2調整至一關閉位置時，基本上自壓縮機1 〇而來之顫動 點壓力可保持穩定。因此，一需要較低流率與高壓縮機壓 力足操作狀況’可藉由調整升壓器圓環4 〇與4 2至—關閉 位置加以滿足。 -20- 本紙張尺度適用中國國家標準（CNS ) A4現格（ 210X297公釐） --L---r---裝-------丨訂 ^------線 (請先閲讀背面之注意事項再填寫本頁) 經濟部中央標準局員工消费合作社印装 ^ϋ,ώ66ό Α7 ___Β7___ 五、發明説明（18 ) _相對於全負荷操作壓力比（例如全負荷的9〇%)而言， 需要低流率與高壓力比之操作狀況，常見於一般狀況中。 在此狀況中’雖然周圍氣溫與室溫會有很大的差別（例如約 5 〇 °F或更多），但是建築物中卻僅有低負荷需要冷卻。因 此，雖然對應濃縮器與蒸發溫度而言，冷卻劑飽和壓力需 要較高的壓縮機壓力比（例如大於約2.5 )，但在建築物 中，僅需有全負荷例如25%之較低流率，即可移除所產生 的熱。 圖15依據本發明，顯示一同時具有可調導葉與可變管路 升壓器之壓縮機之性能圖。可知，一壓縮機的效率時常能 藉由結合調整導葉3 3與升壓器圓環4 0及4 2加以最佳化。 對照圖 1 5 ’ 虛線 1 1 1、π 2、1 13、1 14、1 15 與 1 1 6，為一具 有可變升壓器之壓縮機，在全開位置入口導葉33不同定位 下之性能曲線’然而實線1 〇 !、1 〇2、1 〇3、104與1 05，則為 一具有部分關閉升壓器圓環之壓縮機（在此，關閉位置中約 有40%的初流率），在不同導葉定位下之性能曲線。如熟知 此技術之人所了解，當一壓縮機操作於代表壓縮機性能之 性能曲線之"轉折點"時（如圖1 4之8 1 )，可视為具有最佳 效率。對照圖1 5，舉例來說，依據曲線1 0 4操作之壓縮 機’在最大壓力之〇·7倍與最大流率之0.3倍之操作狀況 下’具有最大效率，此可藉由調整升壓器圓環40與42至一 關閉位置，及調整導葉3 3至1 〇度位置加以完成。 雖然本發明對許多特定實例加以解釋’但必須了解本發 明之精神與範園必須由以下之申請專利範圍來決定。 -21 - 本纸张尺度適用中國國家標準（CNS ) Α4規格（210X297公釐） ---=---r---ί.裝------- 訂^------線 (請先閲讀背面之注意事項再填寫本頁)Please read the% items on the back first and then fill in%. This page_1〇2Μα -__ V. Description of the invention (13 A7 B7 Printed by the shellfish consumer cooperation department of the Central Standards Bureau of the Ministry of Economic Affairs ==, can be fixed on the outer ring 42, and The bearing plate will not accidentally contact the inner ring.-But if the outer cover 34 is installed, the main thread of the rotating thread will drive the bearing plate to contact the inner ring. With the bearing plate properly positioned, the lockable nut 94 can be tightened or loosened. In a preferred example, the bearing plate is made of a super-molecular-molecular plastic material. The invention of this invention—the real money, includes six such pumping directions): a gen-made mechanism, the outer circumference of the inner ring of the concrete is spaced equal to each other. In Fig. 10, a position transmission mechanism 121 for rotating the inner ring 40 on the circumference of the outer ring 42 is described. The inner ring 4G has been fixedly attached to the rack 123 extending radially outward from the inner ring 40. In the geared relationship, the rack is connected to the pinion 124 and driven by a starter 28 via the pinion shaft 126. The starter 128 is selected and controlled so that the inner ring 40 is moved relative to the outer ring 42 in the -first-full-open position and the second-part closed position, as well as any intermediate positions. Pinion # 126 outer cover-The outer cover is covered, and the pinion shaft 126 is sealed from the inner surface 132 of the compressor, and this outer cover 13 () also prevents the fluid in the compressor 10 from passing through the outer cover 30 &.冷却 The coolant fluid in the booster, and the tangential and circumferential loads applied to the inner ring will cause the inner ring to tend to vibrate back and forth in the outer ring. Excessive movement or facial movement of the inner ring will wear the teeth 123 and the pinion gear 124 and cause other workpieces to wear. As discussed earlier, pre-loading the inner ring via the roller assembly prevents the inner ring from moving, as well as chattering under normal operating conditions. In abnormal conditions, such as when operating in a trembling state, an L-level mechanism is required to prevent movement of the inner ring. The present invention provides a transmission positioning system, which uses a shaft to cover the cover 130, and adjusts the relative center position between the pinion and the rack. (Please read the precautions on the back before filling this page.) China National Standard (CNS) A4 specification (210X297 mm) A7 B7 V. Description of the invention (14 Restricts the reverse movement and movement of the inner ring by preventing the backlash between the sector gear and the pinion gear. The outer appearance of the sleeve cover s 125 and The housing centerline 127 is concentric, and the housing inner hole 129 is concentric with the housing inner hole centerline 1 3 丨. In a preferred embodiment of the present invention, the housing centerline 27 and the housing inner hole 29 are offset from each other. 60 inch 1 > Refer to Figure Η, showing the wrench plate 135 and the adjustment slot 134 of the positioning transmission mechanism. After installing the positioning transmission mechanism into the suction cover 31, 'place-a spanner (not shown) across the wrench plate 135 to rotate the transmission positioning Mechanism, remove the backlash between the rack 123 and the pinion 124. Once the minimum backlash is reached, tighten the head screws 133 to fix the positioning mechanism. Once the backlash is eliminated, the inner ring movement trend is can Directly through the gear system, controlled by the starter. The fluid passes through the booster 4-a second part closed position, with respect to the fully open position, the flow rate < flow depends on the booster in the partially closed position, the fluid channel <; Minimum cross-sectional area, for the fully open position, the ratio of the minimum cross-sectional area of the fluid channel (defined by the complementary channel areas 44 and 46). Known as the minimum fluid channel area of `` throat area '', when the booster 4 In the fully open position, it is roughly determined by the minimum diameter of the fluid channel 52 of the inner ring channel 44. When the booster 14 is in the second part closed position, the interface between the inner ring 40 and the outer ring * 2 The width is controlled by 53. For example, if a booster has a minimum area (throat area) in the second part closed position, and / 8 square inches, and in a fully open position, it has a minimum area (throat area) Area) 丨 / 4 square inch leaves flow in the partially closed position. The volume flow rate of the fluid passing through the booster will be 50% of the volume flow rate in the fully open position. When the booster 14 is in the second partially closed position Through the compressor The rate will generally be I / 1 ^ ―-- Order ------ line (please read the precautions on the back before filling out this page) Printed by the Ministry of Economic Affairs Central Bureau of Work and Consumer Cooperatives-17 Ministry of Economic Affairs Central Standards Bureau Shellfish Consumer Cooperative Co., Ltd. ruptures 402666 V. Description of the invention (15) In the fully open position, the fluid flow rate through the compressor 10 is about 0% to 100%. When the second part is in the closed position ( (Figure 4), at least about 10% of the fluid volume in the fully open position, will flow through the booster 14 to prevent excessive thermal heating process, noise, and reduction in compressor efficiency. As a result, the two ring sections rotate relatively The amount is limited by the amount of rotation required to make a second part closed position effective, that is, the two rings cannot be adjusted to completely close the fluid flow between them. The angle of rotation allowed between the two rings depends on the fully open position between the two rings The intended flow, and the number and volume of the inflow channel regions 4 4, 46 relative to the volume of the circular regions 40 and 42 in the circular regions 40 and 42. 4 'R2 defines the radius to the tip of the impeller, R3 defines the radius of the outer ring 40, and R4 defines the radius of the outer ring. The amount of the inner ring 40 is T = R3-R2, which defines the thickness of the fluid. It must not be too large, so as not to block the intended part of the fluid (for example, 50% of the fluid) passing through the outer channel 46, and the flow of the fluid through the booster 14. Can be effectively controlled. Before any pressure increase occurs, the rotation of the inner ring relative to the outer ring will reduce the throat area of the booster. This will prevent the fluid from accelerating after the pressure increase. Similarly, the smaller the inner ring thickness τ, the more the fluid passes through the partially closed position. The smaller the corner of the booster. Both effects mentioned above will improve compressor efficiency under partial load operating conditions. Referring to Figures 5 and 12, an example of the present invention is shown. A mechanism is provided to provide the inner ring with a correct position corresponding to a first fully open position and a second partially closed position. The cavity 137 is processed on the outer ring 42 towel, and can accommodate the rack 123. The rack ^ is accurately fixed to the inner ring 40 in a convex and concave manner, and the rack is provided with a two-shaped groove 143 adapted to receive the convex portion 139 of the inner ring 40. The inner ring is positioned at the level of ----------------- installed --------. Order (please read the precautions on the back before filling this page) -18 -'^ Printed by the Consumers' Cooperative of the Central Bureau of Standards of the Ministry of Economics-^ 〇26G〇- 5. Description of the invention (16) The ring is used to determine the fully open position, and the two rings are rotated relative to each other until the fluid channel 52 is completely connected with the outer fluid channel 46. If the two rings are in this position and the ring support mechanism is adjusted as described above, the rack is fixed to the inner ring, and the tooth surface 145 is in contact with the full open stop 14 of the cavity 137. At that time, install the screw check (Not shown) through the gear fixing hole 142, and fastened to the screw hole 138 in the inner ring. The rack and cavity have a size to provide a predetermined tightness of the tube booster. For example, in the present Invention-In a preferred embodiment, the cavity 137 is sized so that when the tooth surface 44 contacts the part of the cavity 37 and the stopper 14 1, the difference between the angular width of the rack and the angular width of the cavity reaches the opening position. In this example, the required stroke of the rack is degrees, the rack angular width is 35 degrees, and the corresponding cavity angle width is 45 degrees. You can use a bearing stop between the rack and the cavity to accurately and repeatably position the two bearing stops at the points corresponding to a fully open position and a partially closed position. The starter is also allowed 丨 2 8 Repairing on site without adjusting the position of the inner and outer rings The operation and use of the present invention can be understood by referring to Fig. 13. According to the present invention, Fig. 13 帛 *-the performance of a compressor with a pipeline booster The performance chart of Figure 13 includes a number of performance curves 60, 6, 2, 6, 4, 66, and 68, each corresponding to an unconnected position between the inner and outer ring regions 40 and 42. Each performance curve, such as 6 〇 is characterized by a flutter point, such as 70, which represents the maximum pressure that can be obtained. Operating a compressor at or below the flutter point may cause a facial motion condition, such as the background portion of the present invention In order to illustrate the present invention, for example, the curve 60 may correspond to the -th-total ----------- w clothes ---- * ~ ·-order ^ ------ line (Please read the precautions on the back before filling out this page} -19- Staff Consumption Cooperative of the Central Government Bureau of the Ministry of Economic Affairs, India 40 2666 V. Description of the invention (17) Open position 'Curve 6 2 may correspond to a partially closed position with a differential full open position of 2 degrees, Curve 64 may correspond to a partially closed position with a differential full open position of 4 degrees, and Curve 6 8 may correspond to a differential full open position Partially closed position at 8 degrees. It can be seen that 'adjusting the ring zones 40 and 42 to a closed position has the effect of adjusting the compressor performance curve, such as the vibration point of 70 and 72 to a lower flow rate. So By adjusting the booster ring 40 and 42 to the closed position, the chattering condition during low flow rate demand can be avoided. By comparing the performance chart of a compressor with a variable booster in FIG. In 14, the performance chart of a compressor with only adjustable inlet guide vanes is helpful to understand the present invention. In Fig. 14, the curves 80, 82, and 84 more 8 8 'correspond to the discontinuous positions where the guide vanes 3 3 are gradually closed. It can be seen that closing the guide vane 33 is similar to closing the booster ring regions 40 and 42 and has the effect of reducing the rate of facial movement. In this way, a tremor condition can be avoided by adjusting the inlet guide vanes 33 to the closed position. However, as can be seen from the performance chart of Fig. 14, adjusting the guide vane 33 to the "closed position" further has the effect of reducing the pressure head from the compressor 10 at the tremor point. Therefore, a low flow rate operating condition that requires a higher pressure cannot be satisfied by adjusting the guide vanes 3 3 alone. In comparison, 'the performance graph of Fig. 13' can be used to show that when the pressure booster rings 40 and 42 are adjusted to a closed position, the pressure at the vibration point from the compressor 10 can be kept stable. Therefore, a condition that requires a lower flow rate and a high compressor pressure to be sufficient for the operation condition 'can be satisfied by adjusting the booster ring 40 and 42 to the off position. -20- This paper size is applicable to Chinese National Standard (CNS) A4 now (210X297mm) --L --- r --- installation ------- order ^ ------ line ( Please read the notes on the back before filling in this page) Printed by the Consumer Cooperatives of the Central Standards Bureau of the Ministry of Economic Affairs ^ ϋ, 6666ό Α7 ___ Β7 ___ V. Description of the invention (18) _ Relative to the full load operating pressure ratio (such as full load 9〇 %), Operating conditions that require a low flow rate to a high pressure ratio are common in general conditions. In this condition, 'Although the surrounding air temperature can vary significantly from room temperature (for example, about 50 ° F or more), there is only low load in the building that requires cooling. Therefore, although the refrigerant saturation pressure needs a higher compressor pressure ratio (for example, greater than about 2.5) for the concentrator and evaporation temperature, in a building, only a lower flow rate of full load, such as 25%, is required. To remove the heat generated. FIG. 15 shows a performance diagram of a compressor having an adjustable guide vane and a variable line booster in accordance with the present invention. It can be seen that the efficiency of a compressor can often be optimized by combining the adjustment of the guide vanes 33 and the booster rings 40 and 42. Referring to Fig. 15 ', the dotted line 1 1 1, π 2, 1 13, 1, 1 14, 1 15 and 1 1 6 shows the performance of a compressor with a variable booster at different positions of the inlet guide vanes 33 in the fully open position. The curve 'However, the solid lines 1 0 !, 1 02, 1 03, 104, and 1 05 are compressors with a partially closed booster ring (here, about 40% of the initial flow in the closed position). Rate), performance curve under different guide vane positioning. As known to those skilled in the art, when a compressor is operated at the " turning point " of the performance curve representing the performance of the compressor (as shown in Fig. 14-8), it can be regarded as having the best efficiency. Referring to FIG. 15, for example, a compressor operating according to the curve 104 has a maximum efficiency under an operating condition of 0.7 times the maximum pressure and 0.3 times the maximum flow rate. The device rings 40 and 42 are brought to a closed position, and the guide vanes 33 to 10 degrees are adjusted to complete. Although the present invention explains many specific examples', it must be understood that the spirit and scope of the present invention must be determined by the following patent application scope. -21-This paper size applies Chinese National Standard (CNS) Α4 specification (210X297 mm) --- = --- r --- ί. Packing --------- order ^ ------ line (Please read the notes on the back before filling this page)