1230761 狄、發明說明： [發明所屬之技術領域 旋厂堅縮機之吸入容積與吐出容積之比 可變之可變内容 本發明係關於使螺 ’亦即内容積比成為 機者。 積比式變頻螺旋壓縮 【先前技術】 設定成可變之可變内纟積比式螺 不者（例如，參照特許第3 159762 以往，將上述内容積比 旋型壓縮機，係有如圖7所 號公報）。. 於該可變内容積& +罗 …社 積比式螺紅級缩機中，在有必要變更上 述内容積比之時，丰、在^ 错由步進馬達1令桿2旋轉，並例如使可 變VI閥3後退。此日本，+ θ Λ f ^谷置控制閥4會隨著可變VU^3的後退 而同時後退，當可變ντ 又VI閥3被固定於新的設定位置時，則以 接觸到可變VI閥3之妝能而击庙；门 、 心而再度被固定。如此，上述容量控 制閥4之前端會退後到對纟 ^對應，交動後之内容積比之位置為止 ，而重新規定吐出口 5之開口度。 此種U开y 4 ’上述内容積比，係檢測出以運轉時之轉子 14外π 7内壁所形成之空間即將連通至吐出空間前之壓力 Pdl並以σ又定使该檢測壓力pdl與吐出壓力Pd2之差ΛΡ成為 取小之方式’藉由給予信號至步進馬達1而指定。或者，藉 由以控制以置10傾向解析運轉時之吸入壓力、吐出壓力等 之參數，預、測最適内容積比，並藉由將顯示該最適當内容 積比之值之信號給予至步進馬達1而加以指定。 於上述構成中’由吸入孔6所吸入之流體於外殼7内，藉 88745 1230761 由在公母轉子（未圖示）壓縮後，經吐出口5吐出於吐出口8。 ^該狀態下’作用於可變内容積比式螺旋型壓縮機之負 交八動二’在容量控制必要之時’根據其控制指令，油壓活 基9會前進動作’使容量控制閥4僅前進必要量，故在可變 VI閥3與容量控制閥4間會產生間隙。並且，壓縮途中之流 體，係由可變與容量控制閥4之間隙被分流至吸入側。 亦即，於上述特許第3 1 59762號公報中’以對應在全負荷 能力〇〇〇%負載）時之運轉時之高低壓力條件而成為最高之 壓縮機效率之方式，使由容量控制閥4吐出之_氣體之内 容積比成為可變。 但，揭示於上述以往特許第3 159762號公報中之可變内容 積比式螺旋型壓縮機，具有以下之問題。 1亦即’於上述以往之可變内容積比式螺旋型壓縮機之可 =容積比技術，雖係以對應運轉時之高低壓力條件成為 最高之壓縮機效率> fy. 俄及丰之方式，使由吐出口 5所吐出之壓縮氣體 :内：：比成為可變，但其係對應全負荷能力(嶋負載) 4之。又疋。亚且，於部份負荷能力時（部份負載時），藉由將 [、、佰迷中之*體由可變VI閥3與容量控制閥4之間隙分流至 吸入侧，進行忐力調整（卸載），故有效率差之問題。 另外，由於具備有變更内容積比之可變γι閥3與進行容量 控制之容量控制閥4，故需要個別地具備有内容積比變更時 之可變VI閥3控制機構與容量控制時之容量控制閥4控制機 構，故亦有閥控制機構複雜之問題。 、 【發明内容】 88745 1230761 因此，本發明之目的在於提供對應負荷（運轉條件）而經常 可以最大效率運轉之可變内容積比式螺旋型壓縮機。 為達成上述目的，本發明之可變内容積比式變頻螺旋壓 :機，其特徵為具備有：藉由變更於螺旋壓縮部之壓縮步 驟終了時間點，而使内容積比成為可變之可變内容積比闊 ;驅動旋轉上述螺旋壓縮部之電動機；及對應負荷而控制 上述電動機之旋轉頻率之變頻器。 根據上述構成，於對應負荷而調整壓縮能力之時，可由 變頻器控制電動機之旋轉頻率。如此’可不進行卸載控制 而進行能力調整。並且，以對應被調整之上述電動機之旋 轉頻率之最高壓縮機效率之方式’控制可變内容積比閥之 開度，並設定於螺旋壓縮部之壓縮步驟之終了時點。結果 ’可對應其負荷而經常以最大效率運轉。 μ另外，本發明之可變内容積比式變頻螺旋壓縮機，其特 徵為具備有：根據於上述螺旋壓縮部之吸入側壓力、吐出 側壓力與上述電動機之旋轉頻率，控制上述可變内容積比 閥之開度之控制部。 根據上述構成，於上述可變内容積比時，由控制部 ’根據上述螺旋壓縮部之吸入側壓力及吐出側壓力，與上 述：動機之旋轉頻率，來控制上述可變内容積比閥之開度 。因此，藉由使用預先設定之壓縮比、電動機之旋轉頻率 〃最適内谷積比之關係，可確實且容易地控制上述内容積 使成為對應由上述變頻器控制所調整之上述電動機之 旋轉頻率之最高壓縮機效率。 88745 1230761 【實施方式】 發明之實施形態 以下’以圖示之實施形態詳細說明本發明。圖1係於本實 施形態之可變内容積比式變頻螺旋壓縮機之概略圖。另外 ，圖1A係顯示低内容積比，而圖⑺則顯示高内容積比之情 形。 @ 於圖1，11為電動機，其具有相對於外殼（未圖示）被固定 之定子12，及被固定於主軸14之一端側而旋轉之轉子η。 電動機11係由變頻器15而變頻驅動。上述主軸14之兩端係 以軸承16, 17支持著，而在主軸14之另一端側則安裝有螺旋 轉子1 8。並且，藉由電動機丨丨，當主軸丨4被旋轉時螺旋轉 子1 8纟旋轉，藉由外圍面之螺旋溝（未圖示）可壓縮吸入氣體 。於軸方向具有特定長度之吐出口 2〇, 1設有相對於螺^ 轉子18之外圍面之圓筒狀之滑動閥19，於螺旋轉子18被壓 系侣之氣體係由吐出口 2 0吐出。 於上述滑動閥19之反電動機11側之邊緣面，安裝有藉由 支持板21而可自由地滑動地被支持著的複數個負載22之一 鳊。亚且，各負載22之另一端係被安裝在丨片連結板U上。 於支持板之反螺旋轉子18側之中央表面，設置有汽㈣ ;而在收容於該汽缸24之活塞25之反螺旋轉子⑻則所安裝 之活塞負載26前端，安裝有連結板23。如此，隨著往活塞 25軸方向的移動，通過活塞負_、連結如與負載/ 使知滑動閥19向軸方向移動。 供給於上述汽缸24内之活塞25兩側之作動室以及自其排 88745 Ϊ230761 出之作動流體，係根據來自壓縮部控制器27之控制信號， 由流體控制裝置28所控制。另外，上述流體控制裝置28之 具體構成，只需有於使内容積比下降時，如圖丨八所示使活 f 25移動至螺旋轉子18側，另一方面’於使内容積比上昇 忪，則如圖1B所不使活塞25移動至反螺旋轉子18側之構成 即可，並無特別限定。 .要 於上述構成之可變内容積比式變頻螺旋壓縮機-，對於負 荷之能力調整，係藉由變頻器15對電動機11之旋轉參控制 來進行。因此，於能力調整時沒必要進行卸載控制>即可 :制運轉效率的降低。此外，因可免除進行容量控制之容 量控制閥，故可簡化閥控制機構。 對此上述可變内容積比係為能成為對應運轉狀態之最 高效率.，@由壓縮部控制器27控制滑動閥19之位置。並且 ，於低内容積比指令時，藉由使滑動閥19(亦即，吐出口20 :開始位置)移動至軸方向電動機11側，並加速於壓縮部之 壓、％步驟終了時點’使壓縮氣體儘速吐出。另-方面，於 :内容積比指令時’藉由使滑動閥19(亦即，吐出口20之開 始位置）移動絲方向活塞25側，並延㈣縮部之壓縮步驟 終了時點使壓縮氣體延遲吐出“P，於本實施形態中，藉 由滑動閥19構成上述可變内容積比閥。 並且’如上述，去山ϊ . 田由上述變頻器丨5設定電動機u之旋轉 數，而由壓縮部拎生丨|。 才工制范27設定滑動閥19之位置後，由吸入 口所吸入之氣體合、M ^ 、， 9通過電動機11内被引導至螺旋轉子1 δ。 並且，藉由形成於碑 、不灰轉子18之外圍面之上述螺旋溝被壓 88745 -10- 1230761 縮，並自滑動閥19之吐出口 2〇被吐出。 以下，敘述有關在本實施形態中之電動機11之旋轉數控 制與滑動閥1 9之位置控制。 圖2係顯示於本可變内容積比式變頻螺旋壓縮機之能力 、内谷積比控制系統之圖。於圖2中以被搭載於冷凍機並壓 縮加熱冷媒之螺旋壓縮機3丨為例作說明。 上述冷凍機係依序環狀地連接螺旋壓縮機31、冷凝器Μ 私脹閥33及&發5 34而構成。並且，由螺旋壓縮機3工所 土出之阿服回壓之冷媒，在冷凝器32藉由冷卻水或與空氣 之熱交換而被冷凝，成為低溫高壓之液體冷媒並供給至膨 脹閥33。亚且’在膨脹閥33所減壓之低溫低壓之液體冷媒 ，係在蒸發器34藉由與水之熱交換而被蒸發，成為低壓氣 體並返回螺旋壓縮機31。並且，在蒸發器34所冷卻之冷水 係被使用於冷氣。 _於上述洛發器34之冷媒管上安裝有溫度感應器”，而顯 示來自該溫度感應器35之冷卻水溫Tw之檢測信號，則被輸 入於控制裝置36之旋轉數輸出部37。如此，旋轉數輸出部 37係將根據被輸人之檢測信號之冷卻水溫㈣為負荷側之 貢訊，例如根據與設^溫度之差，計算出為得到所必需之 冷束能力之電動機u之旋轉頻率Hz，並輸出至控制裝置％ 之取適内容積比輸出部38與變頻器15。變頻器⑸系根據上 述所接收之旋轉頻率Hz’控制電動機U之旋轉數。如此， 能進行對負荷之能力調整。 另—方面’於包含上㈣旋轉子18與滑㈣19之螺旋壓 88745 1230761 縮部39之吸入側，安裝有低壓側壓力感應器40，而於吐出 側則安裝有高壓側壓力感應器4 1。並且’顯示由低壓側壓 力感應器40之低壓力LP之檢測信號與顯示由高壓側壓力感 應器41之高壓力HP之檢測信號，係被輸入至最適内容積比 輸出部3 8。如此，最適内容積比輸出部3 8，係基於根據被 輸入之檢測信號之吸入侧之低壓力LP與吐出側之高·'壓力 HP，檢測得知於電動機11之旋轉數設定後之運轉狀況。接 著，根據低壓力LP、高壓力HP與來自旋轉數輸出部37之旋 轉頻率Hz進行演算處理，計算出於目前之旋轉頻率Hz之最 適内容積比並輸出至壓縮部控制器2 7。如此，壓縮部控制 器27會根據上述所接收之内容積比，控制流體控制裝置28 之動作。如此，即能進行對應運轉狀況之内容積比控制 但上述流體控制裝置28之構成，在具有進行與向滑動閥 1 9之軸方向之移動成比例之動作之要素（操作導引閥之外 部驅動馬達等）時’可由上述要素之動作位置，檢測得知滑 動閥19之位置。於此情形，將來自流體控制裝置28之顯示 滑動閥丨9位置SV之檢測信號，通過塵縮部控制器27，或者 直接輸入至最適内容積比輸出部38。並且，於最適内容積 比輪出部38中，根據上述所接收之滑動閥19之位置SV，^ 出現在之内容積比值，而回饋控制最適内容積比值。藉此 ’可進行精度良好之可變内容積比控制。 另外，於上述流體控制裝置28之構成為無法檢測得知滑 MW位置之構成（例如U配管與電磁閥構成）時，最適内 、輪出。”8會先積算出自起動時起之輸出内容積比值 88745 1230761 。亚且，藉由將該積算内容積比值作為現在之内容積比值 ，计异出對最適内容積比值之控制量△v〗，而進行回饋控 制。 、工 圖3係顯示與圖2不同之能力、内容積比控制系統之圖。 於圖3中亦在冷凍機搭載螺旋壓縮機3丨。另外，控制裝置η 與變頻器54係具有與圖2不同之構成。以下，與圖2相同之 構件係附上相同號碼，而主要說明有關控制裝置5 1與變頻 器5 4之動作。 與圖2之情形相同，顯示來自溫度感應器35之冷卻水溫丁w 之檢測信號，係被輸入於控制裝置5丨之旋轉數輸出部52。 又，顯示由低壓側壓力感應器4〇之低壓力Lp之檢測信號， 與顯不由高壓側壓力感應器4丨之高壓力HP之檢測信號，係 被輸入至控制裝置51之最適内容積比輸出部53。並且，藉 由旋轉數輸出部52，根據冷卻水溫Tw，可計算出為得到所 必需之冷凍能力之電動機11之旋轉頻率Hz，再由變頻器54 控制電動機11之旋轉數。如此，能進行對負荷之能力調整。 於本實施形態之變頻器54，係可檢測出上述電動機u之 驅動電壓V與驅動電流A(或者驅動電力w)，並將該檢測出 之艇動電壓V與驅動電流A(或者驅動電力w)送回至旋轉數 輸出部52。並且，藉由旋轉數輸出部52，將上述被計算出 之旋轉頻率Hz、上述所接收到之驅動電壓v與驅動電流A( 或者驅動電力w)，傳送至最適内容積比輸出部53。 如此，上述最適内容積比輸出部5 3，與圖2之情形相同， 根據來自壓力感應器40, 41之低壓力LP及高壓力HP、來自旋 88745 -13 - 1230761 轉數輸出部52之旋躺4S、安·^ t 心員率Hz、與來自流體控制裝置28之滑 動閥19位置s V谁、'舍@ + a 曰 ^處理’計算出對最適内容積比之控 制畺△ V I ，並輸出至壓縮部控制器2 7。 α此外/於本貫施形態巾’可藉由上述最適内容積比輪出 部53 ’記憶由旋轉數輸出部52之驅動電壓ν與驅動電流八( ^者驅動電力W)之變化推移。並且，-邊重複進行上述内 貝動作 邊進仃内容積比控制，以使驅動電壓v與驅 動電流A(或者驅動電力w)成為最小。 之後’與圖2之情形相同，藉由上述壓縮部控制器27,根 據上述接收到之控制量Δνι控制流體控制裝置Μ之動作 ，並回饋控制對應運轉狀況之内容積比。 另外’此時與圖2之情形相同，於上述流體控制裝置28 之構成無法檢測得知滑動閥19位置之構成時，最適内容積 比輸出部53 ’會將積算自起動時起之輸出内容積比值之積 算内容積比值作為現在之内容積比值，並計算出最適内容 積比值之控制量△V I。 雖然，於圖2及圖3所示之控制裝置36,51之最適内容積比 :出：38,53中’係進行演算處理而算.出對最適内容積比之 控制$ △ V 1。但，將來自壓力感應器40之低壓力LP、來 自壓力感應器41之高壓力ΗΡ、來自旋轉數輸出部37,52之旋 轉頻率HZ，依序儲存於記憶體。並且，將低壓力LP、高壓 力册及旋轉頻率Hz，與前次之内容積比動作時之低壓力Lp 、问壓力HP及旋轉頻率Hz相比較，根據該等變化之推移， 亦能求出對最適内容積比之控制量△V工。 88745 12307611230761 D. Description of the invention: [Technical field to which the invention belongs] The ratio of the suction volume to the discharge volume of a spinning mill compactor is variable and variable. The present invention is about making the screw, that is, the content volume ratio, the machine. Product ratio variable frequency screw compression [prior art] Set to a variable variable internal product ratio screw type (for example, refer to Patent No. 3 159762). Bulletin). In this variable inner volume & Luo ... social volume ratio type screw red stage shrinker, when it is necessary to change the above inner volume ratio, Feng and Zao are rotated by the stepper motor 1 and the lever 2 and For example, the variable VI valve 3 is moved backward. In this Japan, + θ Λ f ^ Valley-mounted control valve 4 will simultaneously retreat with the retreat of variable VU ^ 3. When the variable ντ and VI valve 3 are fixed at the new set position, the variable will be touched. The makeup of VI valve 3 can hit the temple; the door and heart are fixed again. In this way, the front end of the above-mentioned volume control valve 4 will be retracted to the position corresponding to the volume ratio after the interaction, and the opening degree of the discharge port 5 will be re-defined. The above-mentioned content ratio of the U open y 4 'is the detection of the pressure Pdl immediately before the space formed by the inner wall of the outer π 7 of the rotor 14 when it is in operation, and the detection pressure pdl and spit are determined by σ. The difference ΔP of the pressure Pd2 becomes a method of taking a small one 'by specifying a signal to the stepping motor 1. Or, by analyzing the parameters such as the suction pressure and the discharge pressure during operation by controlling the setting to 10, predict and measure the optimal inner volume ratio, and give a step to the signal by displaying the value of the optimum inner volume ratio. The motor 1 is designated. In the above structure, the fluid sucked through the suction hole 6 is inside the casing 7 and is compressed by the male and female rotors (not shown) by 88745 1230761, and then discharged through the discharge port 5 through the discharge port 8. ^ In this state, 'Negative cross-action eight-action two acting on variable internal volume ratio type screw compressors'. When the capacity control is necessary', according to its control command, the hydraulic pressure base 9 will move forward to make the capacity control valve 4 Since only the necessary amount is advanced, a gap is generated between the variable VI valve 3 and the capacity control valve 4. In addition, the fluid in the middle of compression is diverted to the suction side through the gap between the variable and volume control valve 4. That is, in the above-mentioned Japanese Patent No. 3 1 59762, 'the capacity control valve 4 is used to achieve the highest compressor efficiency in accordance with the high and low pressure conditions during operation at the full load capacity (000% load). The inner volume ratio of the discharged _ gas becomes variable. However, the variable internal volume ratio type screw compressor disclosed in the above-mentioned conventional patent publication No. 3,159,762 has the following problems. 1 means' in the above-mentioned variable-volume-to-volume-screw compressor's possible = volume ratio technology, although it is the compressor efficiency that is the highest in response to high and low pressure conditions during operation> fy. , So that the compressed gas: in :: ratio discharged from the outlet 5 becomes variable, but it corresponds to the full load capacity (嶋 load) 4. Again. In addition, during partial load capacity (under partial load), the pressure adjustment is performed by shunting the body in [, Baimi from the gap between the variable VI valve 3 and the capacity control valve 4 to the suction side. (Unloading), so there is a problem of poor efficiency. In addition, since the variable gamma valve 3 and the capacity control valve 4 for changing the volume ratio are provided, it is necessary to separately provide the variable VI valve 3 control mechanism and the capacity during volume control when the volume ratio is changed. The control mechanism of the control valve 4 has the problem that the valve control mechanism is complicated. [Contents of the invention] 88745 1230761 Therefore, the object of the present invention is to provide a variable internal volume ratio type screw compressor that can often operate at maximum efficiency in response to the load (operating conditions). In order to achieve the above-mentioned object, the variable content area ratio type variable frequency screw press of the present invention is characterized in that: the content area ratio becomes variable by changing the end time of the compression step in the spiral compression section. Variable internal volume ratio; drive a motor that rotates the spiral compression unit; and an inverter that controls the rotation frequency of the motor in response to a load. According to the above configuration, when the compression capacity is adjusted according to the load, the frequency of rotation of the motor can be controlled by the inverter. In this way, the capacity can be adjusted without performing unloading control. In addition, the opening degree of the variable internal volume ratio valve is controlled in a manner corresponding to the highest compressor efficiency of the above-mentioned rotation frequency of the motor, and is set at the end of the compression step of the spiral compression section. As a result, it can often operate at maximum efficiency in response to its load. In addition, the variable internal volume ratio type variable frequency screw compressor according to the present invention is characterized in that the variable internal volume ratio is controlled based on the suction side pressure, the discharge side pressure of the spiral compression part, and the rotation frequency of the motor. Control part of the valve opening degree. According to the above configuration, when the variable inner volume ratio is changed, the control unit 'controls the opening of the variable inner volume ratio valve based on the suction side pressure and the discharge side pressure of the spiral compression portion and the rotation frequency of the motive force. degree. Therefore, by using the relationship between the preset compression ratio and the rotation frequency of the motor 〃 the optimal inner valley ratio, the above-mentioned internal volume can be reliably and easily controlled so as to correspond to the rotation frequency of the motor adjusted by the inverter control. Maximum compressor efficiency. 88745 1230761 [Embodiments] Embodiments of the invention The present invention will be described in detail below with reference to the embodiments shown in the drawings. Fig. 1 is a schematic diagram of a variable internal volume ratio type variable frequency screw compressor in this embodiment. In addition, Fig. 1A shows a low inner volume ratio, while Fig. 显示 shows a high inner volume ratio. @ 11, 11 is a motor having a stator 12 fixed to a housing (not shown), and a rotor η fixed to one end of the main shaft 14 and rotating. The motor 11 is driven by a frequency converter 15 in a frequency-converted manner. Both ends of the above-mentioned main shaft 14 are supported by bearings 16, 17 and a spiral rotor 18 is mounted on the other end side of the main shaft 14. In addition, with the motor 丨 丨, when the main shaft 丨 4 is rotated, the spiral rotor 1 8 纟 rotates, and the spiral groove (not shown) on the peripheral surface can compress the inhaled gas. A discharge port 20.1 having a specific length in the axial direction is provided with a cylindrical slide valve 19 opposite to the outer surface of the screw rotor 18. The gas system of the compressed rotor 18 is discharged from the discharge port 20. . On the edge surface of the slide valve 19 on the side opposite to the motor 11, one of a plurality of loads 22 supported by the support plate 21 is slidably supported. The other end of each load 22 is mounted on a piece of connecting plate U. On the central surface of the anti-spiral rotor 18 side of the support plate, a steam cymbal is provided; and at the front end of the piston load 26 mounted on the anti-spiral rotor 活塞 of the piston 25 housed in the cylinder 24, a connecting plate 23 is installed. In this way, as the piston 25 moves in the axial direction, the piston valve is moved in the axial direction by the negative and connection of the piston and the load / displacement valve 19. The actuating chambers provided on both sides of the piston 25 in the cylinder 24 and the actuating fluids from the rows 88745 to 230761 are controlled by the fluid control device 28 according to a control signal from the controller 27 of the compression section. In addition, the specific configuration of the fluid control device 28 described above only needs to move the live f 25 to the spiral rotor 18 side as shown in FIG. 8 when the inner volume ratio is decreased, and on the other hand, 'to increase the inner volume ratio 忪As shown in FIG. 1B, the configuration in which the piston 25 is not moved to the side of the anti-helical rotor 18 may be used, and is not particularly limited. For the variable internal volume ratio variable frequency screw compressor of the above structure, the capacity adjustment of the load is performed by the inverter 15 controlling the rotation parameters of the motor 11. Therefore, it is not necessary to perform unloading control when the capacity is adjusted: the reduction of the control operation efficiency. In addition, since the capacity control valve for volume control can be eliminated, the valve control mechanism can be simplified. In this regard, the above-mentioned variable internal volume ratio is the highest efficiency that can be achieved in the corresponding operating state. @The position of the slide valve 19 is controlled by the compression unit controller 27. In addition, when a low internal volume ratio command is issued, the slide valve 19 (that is, the discharge port 20: start position) is moved to the axial direction motor 11 side, and is accelerated to the pressure of the compression portion, and the compression is performed at the end of the step. Gas spit out as soon as possible. On the other hand, at the time of the internal volume ratio command, the compressed gas is delayed by moving the slide valve 19 (that is, the starting position of the discharge port 20) to the side of the piston 25 in the wire direction and delaying the compression step of the constriction Spit out "P. In this embodiment, the above-mentioned variable internal volume ratio valve is constituted by a slide valve 19. And 'as described above, go to the mountain. The field is set by the inverter 5 and the number of rotations of the motor u is compressed.部 拎 生 丨 |. After setting the position of the slide valve 19, the working system 27, the gas inhaled by the suction port, M ^ ,, 9 is guided to the spiral rotor 1 δ through the motor 11. Moreover, by forming The above-mentioned spiral groove on the outer surface of the monument and the ashless rotor 18 is shrunk by 88745 -10- 1230761, and is discharged from the discharge port 20 of the slide valve 19. The rotation of the motor 11 in this embodiment will be described below. The digital control and the position control of the sliding valve 19. Figure 2 is a diagram showing the capacity of the variable internal volume ratio variable frequency screw compressor and the internal valley volume ratio control system. In Figure 2, it is mounted on a freezer and Screw compressor for compression and heating of refrigerant3 丨The above-mentioned refrigerator is constituted by sequentially connecting the screw compressor 31, the condenser M swell valve 33, and & 5 34 in sequence. Furthermore, the freezer was unearthed from the 3rd office of the screw compressor. The back-pressured refrigerant is condensed in the condenser 32 through cooling water or heat exchange with air, and becomes a low-temperature and high-pressure liquid refrigerant and is supplied to the expansion valve 33. The low-temperature and low-pressure The liquid refrigerant is evaporated in the evaporator 34 through heat exchange with water, becomes a low-pressure gas, and returns to the screw compressor 31. The cold water cooled in the evaporator 34 is used for cold air. A temperature sensor is installed on the refrigerant pipe of the device 34, and a detection signal indicating the cooling water temperature Tw from the temperature sensor 35 is input to the rotation number output section 37 of the control device 36. In this way, the rotation number output section 37 is based on the temperature of the cooling water of the input signal of the person being input, as a tributary of the load side. The rotation frequency Hz is output to the appropriate internal volume ratio output section 38 and the inverter 15 of the control device%. The frequency converter controls the number of rotations of the motor U based on the received rotation frequency Hz '. In this way, the ability to adjust the load can be performed. On the other hand, a low-pressure-side pressure sensor 40 is installed on the suction side of the spiral pressure 88745 1230761 of the constriction 39 including the upper rotor 18 and the slipper 19, and a high-pressure side sensor 41 is installed on the discharge side. Further, the detection signal indicating the low pressure LP displayed by the low pressure side pressure sensor 40 and the detection signal indicating the high pressure HP displayed by the high pressure side pressure sensor 41 are input to the optimum inner volume ratio output section 38. In this way, the optimal inner volume ratio output unit 38 is based on the input pressure of the low pressure LP on the suction side and the high pressure HP on the discharge side, and detects the operation status after the rotation number of the motor 11 is set. . Next, calculation is performed based on the low pressure LP, the high pressure HP, and the rotation frequency Hz from the rotation number output section 37, and the optimal inner volume ratio based on the current rotation frequency Hz is calculated and output to the compression section controller 27. In this way, the compression section controller 27 controls the operation of the fluid control device 28 based on the content volume ratio received as described above. In this way, the content-to-volume ratio control can be performed in accordance with the operating conditions. However, the structure of the fluid control device 28 described above has an element that performs an action proportional to the movement in the axial direction of the slide valve 19 (external driving of the pilot valve) Motor, etc.) The position of the slide valve 19 can be detected from the operating position of the above elements. In this case, the detection signal from the display slide valve 9-position SV of the fluid control device 28 is directly inputted to the dust reduction section controller 27 or the optimum inner volume ratio output section 38. In addition, in the optimal inner volume ratio wheel output unit 38, based on the received inner volume ratio of the position SV of the slide valve 19, the optimal inner volume ratio is controlled by feedback control. With this, the variable inner volume ratio control with high accuracy can be performed. In addition, when the configuration of the above-mentioned fluid control device 28 is a configuration in which the position of the sliding MW cannot be detected (for example, the configuration of a U pipe and a solenoid valve), it is optimal to turn out. "8 will first calculate the output content volume ratio value 88745 1230761 since the start. And, by using the accumulated content volume ratio as the current content volume ratio, calculate the control amount △ v for the optimal content volume ratio. The feedback control is performed. Figure 3 is a diagram showing a control system with different capabilities and content-to-volume ratios than that in Figure 2. In Figure 3, a screw compressor 3 丨 is also installed in the refrigerator. In addition, the control device η and the inverter 54 The structure is different from that of Fig. 2. In the following, the same components as those in Fig. 2 are assigned the same numbers, and the operations of the control device 51 and the inverter 5 4 are mainly explained. As in the case of Fig. 2, the display comes from the temperature sensor. The detection signal of the cooling water temperature Dw of the controller 35 is input to the rotation number output section 52 of the control device 5. Furthermore, the detection signal of the low pressure Lp by the low-pressure side pressure sensor 40 is displayed, and the high pressure is not displayed. The detection signal of the high pressure HP of the side pressure sensor 4 is input to the optimal inner volume ratio output section 53 of the control device 51. The rotation number output section 52 can be calculated as the cooling water temperature Tw as The frequency of rotation of the motor 11 to the required refrigeration capacity Hz is controlled by the inverter 54. In this way, the capacity of the load can be adjusted. In the inverter 54 of this embodiment, the above can be detected The driving voltage V and the driving current A (or the driving power w) of the motor u, and the detected boat driving voltage V and the driving current A (or the driving power w) are returned to the rotation number output unit 52. The rotation number output unit 52 transmits the calculated rotation frequency Hz, the received driving voltage v and the driving current A (or driving power w) to the optimum inner volume ratio output unit 53. Thus, the above-mentioned optimum content The product ratio output section 5 3 is the same as that in FIG. 2, according to the low pressure LP and high pressure HP from the pressure sensors 40 and 41, and the rotation lay 4S from the rotary output unit 52 of the rotation 88745 -13-1230761. ^ t heart rate Hz, the position 19 of the sliding valve 19 from the fluid control device 28, s V who, 'shed @ + a ^ processing' calculates the control of the optimal inner volume ratio 畺 △ VI and outputs it to the compression control器 2 7. α Additionally / Yu Guan The shape towel 'can memorize the change of the driving voltage ν and the driving current VIII (the driving power W) of the rotation number output section 52 through the above-mentioned optimal inner volume ratio wheel output section 53. And,-while repeating the above During the operation, the internal volume ratio control is performed so that the driving voltage v and the driving current A (or the driving power w) are minimized. After that, as in the case of FIG. 2, the compression unit controller 27 receives the received data according to the above. The control amount Δνι controls the operation of the fluid control device M, and feedback controls the content-to-product ratio of the corresponding operating conditions. In addition, 'this is the same as the situation in FIG. 2, and the position of the slide valve 19 cannot be detected by the configuration of the fluid control device 28 described above. In the constitution, the optimal content volume ratio output unit 53 ′ calculates the content content ratio value of the output content volume ratio value that is accumulated from the start time as the current content volume ratio value, and calculates the control amount ΔVI of the optimal content volume ratio value. Although, the optimal content volume ratio of the control devices 36 and 51 shown in FIG. 2 and FIG. 3: output: 38, 53 ′ is calculated by calculation. The control of the optimal content volume ratio is $ Δ V 1. However, the low pressure LP from the pressure sensor 40, the high pressure HP from the pressure sensor 41, and the rotation frequency HZ from the rotation number output sections 37, 52 are sequentially stored in the memory. In addition, the low pressure LP, the high pressure book, and the rotation frequency Hz can be compared with the low pressure Lp, the interrogation pressure HP, and the rotation frequency Hz during the previous content ratio operation, and based on the change of these changes, it can also be obtained. The control amount of the optimum internal volume ratio is △ V. 88745 1230761
圖4係顯示以來自上述高壓側壓力感應器4 1之高壓力HP 與來自低壓侧壓力感應器40之低壓力LP(HP/LP)所示之壓 縮比’與最適内容積比之各運轉頻率Hz(= 30 Hz、60 Hz、 90 Hz)的關係。圖4中之直線，為V I = (HP/LP)1/k(k :冷媒 比熱比）所示之理論值。對各冷媒求出如此之壓縮比、最適 内容積比與各運轉頻率Hz之關係，而將上述關係代入以圖2 及圖3所示之最適内容積比輸出部38，53進行演算處理時之 演算式中。 如此’#由上述最適内容積比輸出部3 8，5 3所進行之演 异處理’可確實地計算出對於現在之旋轉頻率HZ2控制量 △ V I 〇 如以上，於本實施形態中，係藉由變頻器-1 5變頻驅動螺 方疋壓縮機中之電動機1變頻驅動。此外，藉由根據來自壓縮 邛&制為27之控制信號以流體控制裝置28控制供給至汽缸 之作動至及自其排出之作動流體，而控制規定吐出開 始位置之滑動閥1 9之軸方向位置。 而對負荷之能力調整，係藉由構成控制裝置36, 51之旋 :數輸：部37,52,將冷卻水溫Tw作為負荷側之資訊，計 又知所必而之冷凍能力之旋轉頻率Hz，再由變頻哭i 5 此54進行控制使電動機U之旋轉數成為該旋轉頻率Η^因 效率*於㈤力调整時之卸載控制之必要性，抑制運轉 f, : 。此外’可免除進行容量控制之容量控制閥， 間化閥控制機構。 卜上述可變内容積比，係藉由上述控制裝置％，5 i 88745 -15 - 1230761 〈攻適内容積比輸出部38, 53,根據吸入側之低壓力Lp、 吐出側之高壓力HP及旋轉頻率Hz進行演算處理，計算出於 現在之旋轉頻率H/之最適内容積比（或Δνι)，以壓縮部控 制器27與流體控制裝置28來設定滑動間19之轴方向位置， 而規定吐出之開始位置。因此，可設定内容積比使其成為 對應電動機11之旋轉頻率Ηζ之最高壓縮機效率。 *因此’根據該實施形態’可將於為進行對負荷之能力調 瘥而控制螺旋壓縮機31之旋轉頻率Ηζ時之壓縮機效率的降 低’抑制到最低限度。 圖5係顯示冷;東能力與壓縮機效率之㈣。橫軸係顯示冷 =力Q’以於併用以往之可變内容積比與卸載控制之可變 2容積比式螺旋壓縮機中，60ΗΖ時之冷滚能力為麵之百 /刀比表示之。另一方面，縱軸則顯示I缩機效率。此外， 使上述壓縮比變化成2.1、3.9、5.5及7 9。 根據圖，併用於本實施彡能 之可,一“. 可變内容積比與變頻控制 了’吏内谷積比式變頻螺 螺方疋壓鈿機之情形，與併用可變内 合積比舁卸載控制之以往之可 情形相較，於100%以下之 '丨螺旋屋縮機之 提高壓縮機效率。並且，二：力叫，任-厂堅縮比皆可 效率，可得到更大::果=能力越大越能提高壓縮機 頻螺旋壓縮機之情形時# 谷積比式交 & ^ 係糟由變頻控制來ϋ彳 能力調整。因此，可進行_上之能力二^負何之 由卸載控制進行對負荇々处a 匕力過正。又’於藉 負何之忐力調整之先前 情形，當然無法進行1〇〇〇/ 先則之螺旋麼縮機之 逍仃100%以上之能力調整。 88745 ' \6 - 1230761 之重要部位構成圖。 圖2係顯示於圖1所示之可變内容積比式變頰螺旋壓縮機 之成力/内谷積比控制系統之圖。 圖3係顯示與圖2不同之能力/内容積比控制系之圖 圖4係顯示與壓縮比與最適内容積比之各運輕 係圖。 之關 圖5係顯示與冷凍能力與壓縮機效率之各壓縮比 圖。 < 關係 圖Α 6Βί丁、顯不於螺旋型壓縮機之内容積與壓力 圖。 、關係 圖7為先别之可戀肉# 艾内4積比式螺旋型壓縮機之剖面 【圖式代表符號說明】 1 步進馬達 2 桿 3 可變VI閥 4 容量控制閥 5 吐出口 7 外殼 8 吐出口 9 油壓活塞 10 控制裝置 11 電動機 12 定子 13 轉子 88745 -18- 1230761 14 主轴 15 變頻器 16, 17 轴承 18 螺旋轉子 19 滑動閥 20 吐出口 21 支持板 22 負載 23 •連結板 24 汽缸 25 活塞 26 活塞負載 27 壓縮部控制器 28 流體控制裝置 31 螺旋壓縮機 32 冷凝器 33 膨脹閥 34 蒸發器 35 溫度感應器 36 控制裝置 37 旋轉數輸出部 38 最適内容積比輸出部 39 螺旋壓縮部 40 低壓側壓力感應器 -19- 88745 1230761 41 高壓側壓力感應器 51 控制裝置 52 旋轉數輸出部 53 最適内容積比輸出部 54 變頻器 88745 -20 -FIG. 4 shows the respective operating frequencies of the compression ratio 'and the optimal inner volume ratio shown by the high pressure HP from the high-pressure pressure sensor 41 and the low pressure LP (HP / LP) from the low-pressure pressure sensor 40. Hz (= 30 Hz, 60 Hz, 90 Hz). The straight line in Figure 4 is the theoretical value shown by V I = (HP / LP) 1 / k (k: refrigerant specific heat ratio). The relationship between the compression ratio, the optimum inner volume ratio and each operating frequency Hz is obtained for each refrigerant, and the above relationship is substituted into the time when the optimum inner volume ratio output units 38 and 53 shown in FIG. 2 and FIG. 3 perform calculation processing. In the calculation formula. In this way, "# the differentiating processing performed by the above-mentioned optimal inner volume ratio output unit 3 8, 5 3" can reliably calculate the control amount △ VI for the current rotation frequency HZ2. As described above, in this embodiment, it is borrowed The inverter 1-5 drives the motor 1 of the square compressor and is driven by the inverter. In addition, the axial direction of the slide valve 19 that regulates the discharge start position is controlled by controlling the operation fluid supplied to and discharged from the cylinder by the fluid control device 28 based on a control signal from compression 邛 & 27. position. The adjustment of the capacity of the load is based on the rotation of the control devices 36, 51: digital input: sections 37, 52. The cooling water temperature Tw is used as the information on the load side, and the rotation frequency of the refrigeration capacity is necessary and known. Hz, and then controlled by the frequency converter i 5 This 54 controls the number of rotations of the motor U to the rotation frequency 因 ^ due to the need for unloading control when the power is adjusted during the force adjustment, to suppress the operation f,:. In addition, it is possible to dispense with a volume control valve and an interval valve control mechanism for volume control. The above-mentioned variable internal volume ratio is based on the above control device, 5 i 88745 -15-1230761 <appropriate internal volume ratio output section 38, 53, according to the low pressure Lp on the suction side, the high pressure HP on the discharge side, and The rotation frequency Hz is subjected to calculation processing to calculate the optimal inner volume ratio (or Δνι) of the current rotation frequency H /. The compression section controller 27 and the fluid control device 28 are used to set the axial position of the sliding room 19, and the discharge is prescribed. The starting position. Therefore, the internal volume ratio can be set to the highest compressor efficiency corresponding to the rotation frequency 旋转 ζ of the motor 11. * Therefore, according to this embodiment, it is possible to minimize the reduction in compressor efficiency when the rotation frequency Ηζ of the screw compressor 31 is controlled to adjust the load capacity. Figure 5 shows the relationship between cold capacity and compressor efficiency. The horizontal axis shows the cold force Q ′, which is expressed by the combination of the conventional variable internal volume ratio and the variable 2-volume ratio screw compressor of the unloading control. The cold rolling capacity at 60ΗZ is expressed as the area / tool ratio. On the other hand, the vertical axis shows the I-reduction efficiency. The compression ratios were changed to 2.1, 3.9, 5.5, and 79. According to the figure, and used in this implementation, one ". Variable internal product ratio and frequency conversion control of the" Inner Valley Product Ratio Type Frequency Conversion Screw Screw Square Press Press "and the combination of variable internal product ratio舁 Compared with the previous situation of unloading control, the efficiency of the compressor is improved below 100%. 丨 The screw compressor can improve the efficiency of the compressor. And, two: force, the contraction ratio can be more efficient, and can be greater: : Result = When the capacity is greater, the compressor frequency can be increased. # Valley product ratio type & ^ The system is adjusted by frequency control to adjust the capacity. Therefore, the ability of _ on the capacity can be ^^ Unloading control is used to adjust the negative force at the negative position a. The force is too positive. Of course, in the previous situation where the negative force is adjusted, of course, it is impossible to perform more than 100% of the spiral screw shrinkage machine. The capacity adjustment of 88745 '\ 6-1230761 is shown in Figure 2. Figure 2 shows the force / inner valley ratio control system of the variable internal volume ratio variable cheek screw compressor shown in Figure 1. Figure 3 shows the capability / content-to-volume ratio control system different from Figure 2. Figure 4 shows the display and compression ratio. The most suitable internal volume ratios are shown in Figure 5. Figure 5 is a graph showing the compression ratios of refrigeration capacity and compressor efficiency. ≪ Relationship diagram Α 6Βί, showing the internal volume and pressure of the spiral compressor Figure. Relational diagram 7 is the section of Xianbei's loveable meat # Aene 4 product ratio spiral compressor [illustration of representative symbols] 1 stepper motor 2 lever 3 variable VI valve 4 capacity control valve 5 spit Outlet 7 Housing 8 Outlet 9 Hydraulic piston 10 Control device 11 Motor 12 Stator 13 Rotor 88745 -18-1230761 14 Main shaft 15 Inverter 16, 17 Bearing 18 Spiral rotor 19 Slide valve 20 Outlet 21 Support plate 22 Load 23 • Link Plate 24 Cylinder 25 Piston 26 Piston load 27 Compression unit controller 28 Fluid control device 31 Screw compressor 32 Condenser 33 Expansion valve 34 Evaporator 35 Temperature sensor 36 Control device 37 Number of revolutions output unit 38 Optimum internal volume ratio output unit 39 Spiral compression section 40 Low-pressure side pressure sensor-19- 88745 1230761 41 High-pressure side pressure sensor 51 Control device 52 Number of rotations output section 53 Appropriate internal volume ratio output 54 Inverter 88745 -20-