玖、發明說明： 【發明所屬之技術領職】 本發明係關於使嫂 之π如壓縮機之吸入容 ，亦即内容積比成為 夺知與吐出容積之比 機者。 合積比式變頻螺旋壓縮 【先前技術】 乂彺將上相容積比設 旋型塵縮機，麵如圖7所 之;1㈣谷積比式螺 號公報）。 ”（例如’参照特許第3Ϊ59762 於該可變内容積比式螺旋 、 尺主/土、、、佰钺中，在有必要變更上 述内容積比之時，藉由半、隹 ^ 错由步進馬達1令桿2旋轉，並例如使可 變VI閥3後退。此時，容晉批岳# 里^工制閥4會隨者可變VI閥3的後退 而同時後退，當可變，3被固定於新的設定位置時，則以 接觸到可變VI閥3之狀態而再度被固定。如此，上述容量控 制閥4之前端會退後到對應變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。 此種情形時，上述内容積比，係檢測出以運轉時之轉子 與外s又7内壁所形成之空間即將連通至吐出空間前之壓力说明 Description of the invention: [Technical Leadership of the Invention] The present invention is about making π like the suction capacity of a compressor, that is, the content volume ratio becomes the ratio between the knowledge and the discharge volume. Integral ratio type variable frequency spiral compression [Prior art] (1) Set the upper phase volume ratio to a rotary dust shrinker, as shown in Figure 7; "(For example, 'Refer to Patent No. 3Ϊ59762 in this variable content volume ratio spiral, ruler / soil ,, and Baiyin. When it is necessary to change the content content ratio mentioned above, step by half, 隹 ^, or wrong. The motor 1 rotates the lever 2 and, for example, makes the variable VI valve 3 back. At this time, the Rong Jin Ping Yue # 里 ^ 工 制 阀 4 will retreat simultaneously with the variable VI valve 3 back, when the variable, 3 When it is fixed at the new setting position, it will be fixed again in the state of contact with the variable VI valve 3. In this way, the front end of the above-mentioned volume control valve 4 will retract to the position corresponding to the content volume ratio after the change ' The opening degree of the discharge port 5 is newly specified. In this case, the above-mentioned internal product ratio is detected as the pressure immediately before the space formed by the rotor and the inner wall of the outer 7 and 7 is connected to the discharge space during operation.
Pdi ’並以設定使該檢測壓力pdl與吐出壓力Ρυ之差成為 最小之方式，藉由給予信號至步進馬達1而指定。或者，藉 由以控制裝置1 〇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 200412397 由在公母轉子（未圖示）厂堅縮後，經吐出口5吐出於吐出口8。 二:嶋下，作用於可變内容積比式螺旋型麼縮機之負 又力―’在容量控制必要之時’根據其控制指♦，油壓活 基9會所進動作’使容量控制閥4僅前進必要量，故在可烧 :間:與容量控制閱4間會產生間隙。並且，壓縮途中之： 虹你由可㈣間3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 能力⑽％負載）時之運轉時之高低壓力條件而成為最高之 昼縮機效率之方式，使由容量控制間4吐出之 容積比成為可變。 鬥 揭丁方、上述以往特許第3丨59762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。 $亦即，於上述以往之可變内容積比式螺旋型壓縮機之可 2谷積tM支術’雖係以對應運轉時之高低壓力條件成為 取冋之壓細機效率之方式’使由吐出口 5所吐出之壓縮氣體 ，内：崎為可變’但其係對應全負荷能力(職負載） 日守之°又疋。亚且，於部份負荷能力時（部份負載時），藉由將 壓縮途中之流體由可變VI閥3與容量控制閥4之間隙：流至 吸入側’進行能力調整（卸載），故有效率差之問題。L 另外，由於具備有變更内容積比之可變VI閥3與進行容量 制之夺里技制閥4 ,故需要個別地具備有内容積比變更時 之可變VI閥3控制機構與容量控制時之容量控制閥4控制機 構，故亦有閥控制機構複雜之問題。 【發明内容】 88745 200412397 匕本务明之目的在於提供對應負 可以最大效I 、（運輅备、件）而經常 m车運轉之可㈣容積比;切_壓縮機。 縮機，比切頻螺旋壓 ^ 具4寸敛為具備有：藉由變更於庐於茂卜* 驟終了時間點 -更於虫“疋堡縮部之摩縮步 …' ，而使内容積比成為可變之可變内 ;驅動綠*舎ί_、4_、，田 谷才貝比閥 上…螺旋壓縮部之電動機；及對應負荷而控制 I笔動钱之旋轉頻率之變頻器。 +根據上述構成，於對應負荷而調整壓縮能力之時 變頻器控制電動機之旋轉頻率。如 而進行能力$敕、， 了不進仃卸载控制 ㈣率之：亚且’以對應被調整之上述電動機之旋 轉頻率之取而壓縮機效率之方式，控制可變内容積比間之 開度’亚設定於螺旋壓縮部之壓縮步驟之終了時點 ，可對應其負荷而經常以最大效率運轉。 另外，本發明之可變内容積比式變頻螺旋麼縮機 徵為具備有：根據於上述螺旋壓縮部之吸入側壓力、:土： 側壓力與上述電動機之旋轉頻率，控制上述可 閥之開度之控制部。 -〜積比 根據上述構成，於上述可變内容積比時，可藉由控制部 ’根據上述螺旋壓縮部之吸入側壓力及吐出側壓力，與上 述電動機之旋轉頻率，來控制上述可變内容積比閥之開度 。^1此，稭由使用預先設定之壓縮比、電動機之旋轉頻率 與最適内容積比之關係，可確實且容易地控制上述内容積 比，使成為對應由上述變頻器控制所調整之上述電動機^ 方疋轉頻率之隶焉壓縮機效率。 88745 200412397 【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。另夕卜 ’圖1A係顯示低内容積比，而圖1B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丨3。 笔動機11係由變頻器1 5而變頻驅動。上述主軸1 4之兩端係 以軸承1 6，1 7支持著，而在主軸14之另一端側則安裝有螺旋 轉子18。並且，藉由電動機u，當主軸14被旋轉時螺旋轉 子18會旋轉，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 20，且設有相對於螺旋 轉子1 8之外圍面之圓筒狀之滑動閥丨9，於螺旋轉子1 8被壓 縮之氣體係由吐出口 20吐出。 於上述滑動閥丨9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 立而。亚且，各負載22之另一端係被安裝在1片連結板23上。 於支持板21之反螺旋轉子18侧之中央表面，設置有汽缸％ :而在收容於該汽缸24之活塞25之反螺旋轉子18側所安裝 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，通過活塞負載26、連結板23與負載22, 使得滑動閥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 200412397 塞25移動至螺旋轉子18側，另一方面 時’則如圖1B所示使活塞25移動至反 即可，並無特別限定。 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^之 具體構成’只f有於使内容積比下降日寺，如目^斤示使活 ’於使内容積比上昇 螺旋轉子18側之構成 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 制 來進行。因此，於能力調整時沒必要進行卸載控制= _運轉效率的降低。此外，因可免除進行容量控制之容 Ή：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，而由壓縮部控制器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2〇 之開始位置）移動至轴方向電動機11側，並加速於壓縮部之 壓縮步驟終了時點，使壓縮氣體儘速吐出。另一方面，於 高内容積比指令時，藉由使滑動閥19(亦即，吐出口2〇之開 始位置）移動至軸方向活塞25側，並延遲壓縮 終了時點使壓縮氣體延遲吐出十於本實施形態 由滑動閥19構成上述可變内容積比閥。 並且，如上述，當由上述變頻器15設定電動機11之旋轉 數，而由壓縮部控制器27設定滑動閥19之位置後，由吸入 口所吸入之氣體會通過電動機！ i内被引導至螺旋轉子1 8。 並且’藉由形成於螺旋轉子18之外圍面之上述螺旋溝被壓 88745 -10- 200412397 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丨1之旋轉數控 制與滑動閥1 9之位置控制。 圖2係纟、、員不於本可瓷内容積比式變頻螺旋壓縮機之能力 、内容積比控㈣、統之圖。於圖2中以被搭載於冷康機並壓 縮加熱冷媒之螺旋壓縮機3丨為例作說明。 上述冷埭機係依序環狀地連接螺旋壓縮機3卜冷凝器32 、膨脹閥33及蒸發器34而構成。並且，由螺旋壓縮機31所 吐出=高溫高μ之冷媒’在冷凝器32藉由冷卻水或與空氣 <、、、又換而被〜’成為低溫高壓之液體冷媒並供給至膨 服間33。並且，在膨脹閥33所減星之低溫低麼之液體冷媒 ’係在蒸發器3 4藉由鱼水$勒丄^、丄# JC之熱父換而被瘵發，成為低壓氣 體並返.回螺旋壓縮機3丨。並 I且 在瘵發益3 4所冷卻之冷水 係被使用於冷氣。 —於上述蒸發器34之冷媒管上安裝有溫度感應器”，而顯 不來自该溫度感應器35之冷卻水溫Tw之檢測信號，則被輸 入於控制裝置3 6之旋轉數輸出邻） y 邛37。如此，旋轉數輸出部 3 7係將根據被輸入之檢測作 — 列乜唬之冷部水溫7^乍為負荷側之 貧訊，例如根據與設定溫度之 °十^出為得到所必需之 冷;東能力之電動機丨丨之旋轉頻 曰、 貝手Hz亚輸出至控制裝置36 之最適内容積比輸出部3 8盥變 、丄、 ，、又頻為15。變頻器15係根據上 ϋ所接收之$疋轉頻率Hz，控制雷私撼 ^k剩兒動機11之旋轉數。如此， 月匕進行對負荷之能力調整。 另方面，於包含上述螺旋轉子18與滑動閥19之螺旋壓 m45 200412397 縮部3 9之吸入側，安裝有低壓側壓力感應器4 0，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4 1之咼壓力HP之檢測信號，係被輸入至最適内容積比 輸出部38。如此，最適内容積比輸出部38，係基於根據被 輸入之檢測信號之吸入側之低壓力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進行异處理，汁异出於目前之旋轉頻率Η?之最 適内容積比並輸出至壓縮部控制器27。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μ 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_ 19之軸方向之移動成比例之動作之要素(操料引閥之外 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 滑動間位置SV之檢測信號，通過壓縮部控制哭27,或者 入至最適内容積比輸出部38。並且，於最適内容積 匕輸出部38中’根據上述所接收之滑動_之位置^，求 出現在之⑽積比值，而回饋控 ，可推广姓点ώ ^^積比值。藉此 進仃粕度良好之可變内容積比控制。 另外，於上述流體㈣裝置28之構 動閥1 9位詈之媸士 <办丨上 …决才双測仔知滑 ^ 構成(例如’以配管與電磁閥構成)日士… 合積比輸出部38會先積算出自起動 ·"取、内 守起之輪出内容積比值 88745 200412397 。亚且，II由將該積算内容積比值作為現在之内容積比值 制計算出對最適内容積比值之控制量m，而進行回饋控 圖3係顯示盥圖2不印夕& ^ ^ _ /、口不门之此力、内容積比控制系統之圖。 於圖3中亦在冷;東機搭載螺旋壓縮機31。料’控制裝m 與變頻器54係具有與圖2不同之構成。以下，與圖2相同之 料係附上相同號碼，而主要說明有關控制裝置Η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〜 之檢測信號，係被輸入於控制裝置51之旋轉數輸出部W。 又頌不由低壓側壓力感應器40之低壓力LP之檢測信號， 與顯示由高壓侧壓力感應器41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^，可計算出為得到^ 必需之冷凍能力之電動機丨丨之旋轉頻率Hz，再由變頻器Μ 控制電動機11之旋轉數。如此，能進行對負荷之能力調整。 於本貝施形怨之變頻器54，係可檢測出上述電動機丨丨之 驅動電壓V與驅動電流A(或者驅動電力W)，並將該檢測出 之驅動電壓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53，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 200412397 轉數輸出部5 2之旋韓賴i 動闊―進行;=、與來自流體㈣ 制量…，並輪出至；?/計算㈣最相容積比之控 别出至昼縮部控制器27。 此外’於本實施形態中’可藉由上述最適内容積比輸出 部53，記憶由旋轉數 、〜槓比輸出 數輸出邛52之驅動電壓V與驅動電流Αί 或者驅動電力W)之變化推移。並且 =Α( ^ YV Ah # k更设進订上述内 邊進行内容積比控制，以使驅動電壓v盘驅 動電流A(或者驅動電力w)成為最小。Pdi 'is specified by giving a signal to the stepping motor 1 so that the difference between the detected pressure pdl and the discharge pressure Pυ is minimized. Alternatively, by analyzing parameters such as the suction pressure and the discharge pressure during operation with the control device 10 tendency, the optimum inner volume ratio is predicted, and a signal showing the value of the optimum inner volume ratio is given to the stepping motor 1 And specify. In the above configuration, the fluid sucked through the suction hole 6 is inside the casing 7 and is condensed at the male and female rotor (not shown) factory by 88745 200412397, and then discharged through the discharge port 5 out of the discharge port 8. Two: Your Majesty, acting on the negative and powerful force of the variable internal volume ratio spiral type shrinking machine-'when the capacity control is necessary' according to its control instructions, the hydraulic pressure base 9 moves forward to make the capacity control valve 4 only advances the necessary amount, so there will be a gap between burnable: and: and capacity control. And, in the middle of compression: Hong You is diverted to the suction side from the gap between Kojima 3 and the capacity control valve 4. That is, in the above-mentioned Japanese Patent No. 3 1 59762, the capacity of the capacity control room 4 is spit out in such a manner as to maximize the efficiency of the daytime shrinkage machine in accordance with the high and low pressure conditions during operation at full capacity (% load). The volume ratio becomes variable. The variable internal volume ratio type screw compressor in the above-mentioned conventional patent publication No. 3,597,62 has the following problems. In other words, in the above-mentioned conventional variable internal volume ratio type spiral compressor, the 2-gold product tM technique 'is a way to achieve the efficiency of the compactor according to the high and low pressure conditions during operation.' The compressed gas discharged from the outlet 5 is internal: Saki is variable, but it corresponds to the full load capacity (job load). At the time of partial load capacity (partial load), the capacity adjustment (unloading) is performed by passing the fluid in the compression process from the gap between the variable VI valve 3 and the capacity control valve 4 to the suction side, so There is a problem of poor efficiency. L In addition, since the variable VI valve 3 with a change of the internal volume ratio and the ripping technology valve 4 of the capacity system are provided, it is necessary to separately provide the variable VI valve 3 control mechanism and the capacity control when the internal volume ratio is changed. The capacity control valve 4 controls the mechanism at the time, so there is also a problem that the valve control mechanism is complicated. [Summary of the Invention] The purpose of 88745 200412397 is to provide the volume ratio that can be used to reduce the maximum efficiency I, (transport equipment, parts) and often m cars; cut _ compressor. Shrinking machine, than the frequency-cutting spiral pressure ^ has a 4-inch convergence to have: by changing the time at the end of Lu Yumaobu *-more than the "steps of the shrinkage of the fortress ...", so that the content volume The ratio becomes variable and variable inside; the motor that drives the green * 舎 ί_, 4_, and Tani Bebe valve ... the screw compression part; and the inverter that controls the rotation frequency of I penny in response to the load. + According to the above The structure controls the rotation frequency of the motor when the compression capacity is adjusted in response to the load. If the capacity is $ 敕, the rate of unloading control is not controlled: Yaer 'corresponds to the above-mentioned motor's rotation frequency. In the way of compressor efficiency, the opening degree of the variable internal volume ratio is controlled to be set at the end of the compression step of the spiral compression section, and it can often be operated at maximum efficiency in accordance with its load. In addition, the invention can The variable internal volume ratio type frequency conversion screw compressor is equipped with a control unit that controls the opening degree of the valve according to the suction side pressure of the spiral compression part, the earth pressure, and the rotation frequency of the motor. ~ The product ratio is based on the above configuration. When the variable internal product ratio is used, the variable internal product ratio can be controlled by the control unit according to the pressure on the suction side and the pressure on the discharge side of the spiral compression unit and the rotation frequency of the motor. The opening degree of the valve. ^ 1 Therefore, by using the relationship between the preset compression ratio, the rotation frequency of the motor, and the optimal internal volume ratio, the above internal volume ratio can be reliably and easily controlled so as to correspond to the above-mentioned inverter control unit. The adjusted efficiency of the above-mentioned electric motor ^ square rotation frequency of the compressor. 88745 200412397 [Embodiment] Embodiments of the invention The invention will be described in detail below with the illustrated embodiment. Figure 1 shows the variable content of this embodiment. The schematic diagram of the product ratio type variable frequency screw compressor. In addition, FIG. 1A shows a low content product ratio, and FIG. 1B shows a case of a high content product ratio. (Not shown) The stator 12 is fixed, and the rotor is fixed to one end of the main shaft 14 and rotates. The pencil 11 is driven by a frequency converter 15 and driven by a frequency converter. Both ends of 14 are supported by bearings 16 and 17 and a spiral rotor 18 is mounted on the other end side of the main shaft 14. Furthermore, with the motor u, when the main shaft 14 is rotated, the spiral rotor 18 will rotate, The spiral groove (not shown) on the outer surface can compress the inhaled gas. The discharge port 20 has a specific length in the axial direction, and a cylindrical slide valve with respect to the outer surface of the spiral rotor 18 is provided. The compressed gas system in the spiral rotor 18 is discharged from the discharge port 20. On the edge surface of the slide valve 9 opposite to the motor 11 side, a plurality of supportable plates 21 are provided to be slidably supported by the support plate 21. One of the loads 22 stands. The other end of each of the loads 22 is mounted on a connecting plate 23. A cylinder is provided on the central surface of the support plate 21 on the side of the reverse spiral rotor 18: A connecting plate 23 is mounted on the front end of the piston load 26 mounted on the side of the counter-spiral rotor 18 of the piston 25 of the cylinder 24. In this way, as the piston 25 moves in the axial direction, the piston load 26, the connecting plate 23, and the load 22 cause the slide valve 19 to move in the axial direction. The operating chambers on both sides of the piston 25 supplied to the above-mentioned cylinder 24 and the plug 25 from its row 88745 200412397 plug 25 are moved to the side of the spiral rotor 18, on the other hand, as shown in FIG. 1B, the piston 25 may be moved to the opposite direction, and It is not particularly limited. The produced working fluid 'is controlled by the fluid control device 28 based on a control signal from the compression section controller 27. In addition, the specific configuration of the above-mentioned fluid control device ^ is only used to reduce the internal volume ratio, and as shown in the figure, the structure of the spiral rotor 18 on the side of the spiral rotor 18 is used to change the internal volume ratio. The volume ratio variable frequency screw compressor is adjusted for load capacity by the inverter 15 to the motor system. Therefore, it is not necessary to perform unloading control during capacity adjustment = _ reduction in operating efficiency. In addition, since the capacity for volume control can be eliminated: control valve, the valve control mechanism can be simplified. In this regard, the above-mentioned variable inner volume ratio is the highest efficiency that can be achieved in the corresponding operating state, and the position of the slide valve 19 is controlled by the compression unit controller 27: and when the low inner volume ratio is commanded, the slide valve 19 is made (That is, the starting position of the discharge port 20) is moved to the axial direction motor 11 side, and is accelerated to the end of the compression step of the compression section, so that the compressed gas is discharged as quickly as possible. On the other hand, when a high internal volume ratio command is issued, the slide valve 19 (that is, the starting position of the discharge port 20) is moved to the side of the piston 25 in the axial direction, and the compressed gas is delayed to be discharged ten times at the end of the delayed compression. In the present embodiment, the above-mentioned variable inner volume ratio valve is constituted by a slide valve 19. And, as mentioned above, when the number of rotations of the motor 11 is set by the inverter 15 and the position of the slide valve 19 is set by the compression controller 27, the gas sucked through the suction port will pass through the motor! Inside i is guided to the helical rotor 18. Further, "the spiral groove is compressed 88745-10--10-200412397 formed by the above-mentioned spiral groove formed on the peripheral surface of the spiral rotor 18" and is discharged from the discharge port 20 of the slide valve 19. In the following, the rotary numerical control of the motor 1 and the position control of the slide valve 19 in this embodiment will be described. Figure 2 is a diagram of the capacity, content ratio control, and system of this product. In Fig. 2, a screw compressor 3, which is mounted on a cold machine and compresses and heats a refrigerant, is taken as an example for illustration. The cold heading machine is configured by sequentially connecting the screw compressor 3, the condenser 32, the expansion valve 33, and the evaporator 34 in an annular manner. In addition, the refrigerant discharged from the screw compressor 31 = high temperature and high μ 'is cooled to low temperature and high pressure liquid refrigerant in the condenser 32 by cooling water or air <, ..., and is supplied to the expansion room. 33. In addition, the low-temperature low-temperature liquid refrigerant reduced by the expansion valve 33 is circulated in the evaporator 34 by the heat father of fish water $ 勒 丄 ^, 丄 # JC, and becomes a low-pressure gas and returns. Compressor 3 丨. In addition, the cold water system cooled in 瘵 FAY 34 is used for cold air. — A temperature sensor is installed on the refrigerant pipe of the above-mentioned evaporator 34 ”, and a detection signal indicating the cooling water temperature Tw from the temperature sensor 35 is input to the rotation number output neighbor of the control device 36) y邛 37. In this way, the rotation number output section 3 7 will be based on the input detection—column water temperature of the cold section 7 ^ is the lean signal on the load side, for example, it is obtained by the temperature of the set temperature. Necessary cooling; East-capable electric motor 丨 丨 Rotating frequency, output frequency of the sub-Hz Hz to the control device 36, the optimum internal volume ratio output section 3 8 盥, 盥, 、, and frequency 15. The inverter 15 series According to the $ Hz rotation frequency Hz received by the upper engine, the number of rotations of the motor 11 is controlled. In this way, the moon dagger adjusts the load capacity. On the other hand, the spiral rotor 18 and the sliding valve 19 are included. Spiral pressure m45 200412397 The suction side of the constriction 39 is equipped with a low-pressure-side pressure sensor 40, and the discharge side is equipped with a high-pressure-side pressure sensor 41. Also, the low-pressure side pressure sensor 40 is displayed. Detection signal and display of pressure LP The detection signal of the pressure HP of the force sensor 41 is input to the optimum inner volume ratio output unit 38. Thus, the optimum inner volume ratio output unit 38 is based on the low pressure LP on the suction side based on the input detection signal. The high pressure HP on the discharge side is detected to determine the operating condition after the number of rotations of the motor 11 is set. Then, different processing is performed based on the low pressure LP, the high pressure HP, and the rotation frequency Hz from the number of rotations output section 37. The optimal inner volume ratio of the current rotation frequency is output to the compression unit controller 27. In this way, the compression unit controller 27 controls the operation of the fluid control device μ according to the received inner volume ratio. It is possible to perform internal volume ratio control according to 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 direction of the axis of the sliding _ 19 (external drive motor of the pilot valve, etc.) At this time, the position of the slide valve 19 can be known from the operating position of the above elements. In this case, the detection signal from the fluid control device 28 indicating the position SV of the slide is communicated. The over-compression unit controls the cry 27, or enters the optimal inner volume ratio output unit 38. Further, in the optimal inner volume output unit 38, 'according to the position of the sliding _ received above, ^, find the volume ratio that appears in it, and Feedback control can promote the product ratio of surnames. This can be used to control the variable content ratio with a good degree of content. In addition, the 9th position of the actuator of the fluid valve 28 of the fluid control device丨 Up ... It ’s only double-tested. It ’s the structure (for example, 'composed of piping and solenoid valve') .... The total output ratio unit 38 first calculates the ratio of the content of the round-out content from the start and the inner guard. 88745 200412397. And, II calculates the control amount m of the optimal content volume ratio by using the accumulated content volume ratio as the current content volume ratio system, and gives feedback control. Figure 3 shows the bathroom image 2 without printing & ^ ^ _ /, Diagram of this force, content volume ratio control system. It is also cold in FIG. 3; Toki is equipped with a screw compressor 31. The control device m and the inverter 54 are different from those shown in FIG. 2. In the following, the same materials as in Fig. 2 are assigned the same numbers, and the operations of the control device Η and the inverter 54 are mainly explained. As in the case of FIG. 2, the detection signal showing the cooling water temperature from the temperature sensor 35 is input to the rotation number output unit W of the control device 51. The detection signal indicating the low pressure LP of the low-pressure-side pressure sensor 40 and the detection signal indicating the high-pressure HP of the high-pressure-side pressure sensor 41 are input to the optimal inner volume ratio output section 53 of the control device 51. In addition, based on the cooling water temperature ^, the rotation number output unit 52 'can calculate the rotation frequency Hz of the motor 丨 丨 necessary to obtain ^, and the frequency of rotation of the motor 11 is controlled by the inverter M. In this way, the ability to adjust the load can be performed. Inverter 54 which is embarrassed by Bembe, can detect the driving voltage V and driving current A (or driving power W) of the above-mentioned motor, and compare the detected driving voltage V and driving current a (or driving The power w) is returned to the rotation number output section 52. Then, the rotation frequency output unit 52 transmits the calculated rotation frequency Hz, the received drive voltage v and drive current A (or drive power W) to the optimum inner volume ratio output unit 53. In this way, the above-mentioned optimal inner volume ratio output section 53 is the same as the case of FIG. 2, according to the low pressure LP and high pressure HP from the pressure sensors 40 and 41, and the rotation from the rotary output section 52 of the rotary number 88745 200412397. Move wide-proceed; =, and the amount of control from the fluid ..., and turn out;? / Calculation of the most phase volume ratio of the control to the day shrinkage controller 27. In addition, in the present embodiment, the above-mentioned optimum inner volume ratio output unit 53 can memorize and change the change in the driving voltage V and the driving current A or the driving power W by the number of rotations and the output ratio of the output ratio 邛 52. And = Α (^ YV Ah # k is set to perform the inner volume ratio control in order to minimize the drive voltage v drive current A (or drive power w).
之後，與圖2之情形相同，藉由上述壓縮部控制器27,根 據上述接收到之批制旦A 、， 工里△ V 1控制流體控制裝置28之動作 ，亚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^ 之構成無法檢測得知滑動閥19位置之構成時，最適内容積 :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 才工制里△ V I 。但，將來自壓力感應器4〇之低壓力、來 自壓力感應器4!之高壓力HP、來自旋轉數輪出部37,52之旋 轉頻率Hz，依序儲存於記憶體。並且，將低麼力Lp、高麼 力HP及旋轉頻率Hz ’與前次之内容積比動作時之低壓力 、高壓力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 I。 88745 14 200412397 圖4係顯示以來自上述高壓侧壓力感應器4丨之高壓力HP 與來自低壓側壓力感應器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(二30 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’藉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Hz之控制量 △ VI。 如以上，於本實施形態中，係藉由變頻器1 5變頻驅動螺 旋壓縮機中之電動機丨變頻驅動。此外，藉由根據來自壓縮 部控制器27之控制信號以流體控制裝置28控制供給至汽缸 24内之作動室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19之軸方向位置。 而對負荷之能力調整，係藉由構成控制裝置36，5丨之旋 轉數輪出部37’ 52’將冷卻水溫Tw作為負荷側之資訊，計 ^出彳又得所必需之冷凍能力之旋轉頻率，再由變頻器1 5 ，54進行控制使電動機u之旋轉數成為該旋轉頻率。因 此，可免除於能力調整時之卸載控制之必要性，抑制運轉 ί率之降低° Λ外’可㈣進行容量控制之容量控制閥， 簡化閥控制機構。After that, as in the case of FIG. 2, the above-mentioned compression unit controller 27 controls the operation of the fluid control device 28 according to the batches A and D received above, and the content of the sub-feedback control corresponding to the operating conditions. Product ratio. In addition, at this time, the situation is the same as that in FIG. 2. When the structure of the above-mentioned fluid control device ^ cannot detect the configuration of the position of the slide valve 19, the optimal internal volume: the output unit 53 ′ will calculate the output internal volume from the time of starting. The accumulated content ratio of the ratio is used as the current content volume ratio, and the control amount ΔVI of the optimal content volume ratio is calculated. Although the optimal content volume ratio of the control devices 36 and 51 shown in Figs. 2 and 3 is shown in: 38, 53, the calculation process to calculate the optimal content volume ratio △ V I is performed. However, the low pressure from the pressure sensor 40, the high pressure HP from the pressure sensor 4 !, and the rotation frequency Hz from the rotary wheel output 37, 52 are sequentially stored in the memory. In addition, comparing the low pressure Lp, high HP HP, and rotation frequency Hz 'with the low pressure, high pressure HP, and rotation frequency Hz during the previous content ratio operation, the change can also be calculated based on these changes. The control amount △ VI for the optimal inner volume ratio is obtained. 88745 14 200412397 Figure 4 shows the compression ratio shown by the high pressure HP from the high pressure side pressure sensor 4 and the low pressure LP (HP / LP) from the low pressure side pressure sensor 40, and the optimal inner volume ratio. The relationship between each operating frequency Hz (two 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 units 3 8, 5 3' can reliably calculate the control amount ΔVI for the current rotation frequency Hz. As described above, in the present embodiment, the motor in the screw compressor is driven by a frequency converter of a frequency converter 15 and driven by a frequency converter. In addition, according to a control signal from the compression section controller 27, the fluid control device 28 controls the operating chamber supplied to the cylinder 24 and the operating fluid discharged therefrom, thereby controlling the axial position of the slide valve 19 that specifies the discharge start position. . The ability to adjust the load is based on the information on the load side by using the cooling water temperature Tw as the information on the load side through the rotating number wheel output section 37 '52' of the control device 36, 5 丨 to calculate the necessary refrigeration capacity. The rotation frequency is controlled by the inverters 15 and 54 so that the number of rotations of the motor u becomes the rotation frequency. Therefore, the necessity of unloading control during capacity adjustment can be eliminated, and the reduction of the operation rate can be suppressed. In addition to the capacity control valve that can perform volume control, the valve control mechanism is simplified.
此外’上述可變内容積比，係藉由上述控制裝置乂，W 88745 200412397 之最適内容積比輸出部3 8，53，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Hz之最適内容積比（或Δν I )，以壓縮部控 制器27與流體控制裝置28來設定滑動閥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Hz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 整而控制螺旋壓縮機3 1之旋轉頻率Hz時之壓縮機效率的降 低’抑制到最低限度。 圖5係顯示冷凍能力與壓縮機效率之關係。橫軸係顯示冷 凍能力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，60Hz時之冷;東能力為1〇〇%之百 分比表示之。另一方面，縱軸則顯示壓縮機效率。此外， 使上述壓縮比變化成2 · 1、3.9、5 · 5及7 · 9。 很像圖，併用於本實施形態之可變内容積比與變頻控 :可變内容積比式變頻螺旋壓縮機之情形，與併 鐵 令積比與卸載控制之以往之可變内衮^ μ + 十主^ “ 」又内夺積比式螺旋壓縮機 月形相較，於1GG%以下之冷;東能力q時，任m 提高壓縮機效率。並且 i、.伯t皆 效率，可得到更大 力越大越能提高壓縮 之效果。另外，於本可變内衮并卜+ 頻螺旋壓縮機之情形時積比式 能力調整。因此，可頻控制來進行對負荷 b可進行1〇0%以上之能 由卸載控制進行對参# °。疋。又，於 情形，當然無法進行 λ 】之&旋壓縮機' 〇 /〇以上之能力調整。 88745 16- 200412397 但’於螺旋壓縮機之情形時，由於即使在相同壓力條件 下亦會因旋轉頻率而產生内壓差，故會存在有對應各頻率 之敢適内谷積比之值。圖6係顯示於頻率3〇 ^2時（圖6a)與 頻率90 Hz時（圖6B)之内容積與壓力之關係。圖中虛線係顯 示於將内谷積比固定於頻率6 〇 Hz時之最適内容積比值之 固定内容積比之情形時，其内容積與壓力之關係曲線。又 ，一點叙想線係顯示於理論隔熱壓縮時之内容積與壓力之 關係曲線。於上述固定内容積比中，於頻率3 〇 Hz時，在時 點（A)發生壓縮不足，壓力急速地減少。又，於頻率出 曰才’在日^點（B)發生過壓縮，壓力則會較理論值增大許多。 由以上得知，無法單純地適用變頻器於螺旋型壓縮機之容 量控制。 但，如本實施形態，藉由設定成可變内容積比，則如以 實線所示，於固定内容積比時，可免除發生於頻率3〇Hz時 之壓縮不足，並同時可縮小壓力變動之幅度。又，於固定 内容積比時，在頻率90 Hz之情形下，可免除發生之過壓縮 並縮小壓力變動之幅度。 另外，於上述實施形態中，雖係以應用於冷凍機之情形 為例，說明本可變内容積比式變頻螺旋壓縮機之能力、内 谷積比控制糸統。但’本發明並未限定於此。只要是於圖2 及圖3，被輸入於控制裝置36，51之旋轉數輸出部37，52之 檢測信號，為表示負荷之狀態之信號即可。 【圖式簡單說明】 圖1A、1B係於本發明之可變内容積比式變頻螺旋壓縮機 88745 . 17 . 200412397 之重要部位構成圖。 圖2係顯示於圖丨所示之可變内容積比式變頻螺旋壓縮機 之fb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係顯不與壓縮比與最適内容積比之各運轉頻率之關 係圖。 圖 〇 圖 圖5 %員不βίί冷；金处；t »- 。 /、 此力舁壓縮機效率之各壓縮比之關係 圖6 A、6B係顯#於螺旋型壓 縮機之内容積與壓力之關係 圖7為先 別之可變内容 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 疋子 13 轉子 壓縮機之剖面圖 88745 ' 18- 200412397 14 主軸 15 變頻器 16，17 軸承 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 活基負載 27 壓縮部控制器 28 流體控制裝置 31 螺旋壓縮機 3 2 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In addition, the above-mentioned variable internal volume ratio is determined by the above-mentioned control device, W 88745 200412397, the optimal 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. Perform calculation processing to calculate the optimal internal volume ratio (or Δν I) based on the current rotation frequency Hz, and set the axial position of the slide valve 19 with the compression controller 27 and the fluid control device 28 to specify the start position for ejection . Therefore, the internal volume ratio can be set to the highest compressor efficiency corresponding to the rotation frequency Hz of the motor 11. Therefore, according to this embodiment, it is possible to minimize the reduction in compressor efficiency when the rotation frequency Hz of the screw compressor 31 is controlled in order to adjust the load capacity. Figure 5 shows the relationship between refrigeration capacity and compressor efficiency. The horizontal axis shows the refrigeration capacity Q ', which is the combination of the conventional variable volume ratio and unloading control of a variable 2-volume ratio screw compressor at 60 Hz; the eastern capacity is expressed as a percentage of 100%. On the other hand, the vertical axis shows compressor efficiency. The compression ratio was changed to 2 · 1, 3.9, 5 · 5 and 7 · 9. Much like the figure, and used for the variable internal product ratio and variable frequency control of this embodiment: the variable internal product ratio type variable frequency screw compressor, and the conventional variable internal ratio of the combined product ratio and unloading control ^ μ + Ten Masters ^ “” The internal shape of the screw compressor is colder than 1GG%. When the capacity is q, let m increase the compressor efficiency. And i and .bot are both efficient. The stronger the force, the greater the compression effect. In addition, in the case of this variable internal and parallel + frequency screw compressor, the capacity ratio adjustment is adjusted. Therefore, the frequency control can be used to perform load control for more than 100%. The unloading control can be used for reference. Alas. Moreover, in this case, of course, it is impossible to adjust the capacity of & rotary compressor 'above 0 / 〇. 88745 16- 200412397 However, in the case of a screw compressor, since the internal pressure difference will occur due to the rotation frequency even under the same pressure condition, there will be values of the courageous inner valley ratio corresponding to each frequency. Figure 6 shows the relationship between the inner volume and pressure at a frequency of 30 ^ 2 (Figure 6a) and at a frequency of 90 Hz (Figure 6B). The dashed line in the figure shows the relationship between the internal volume and pressure when the internal internal volume ratio is fixed at the fixed internal volume ratio of the optimal internal volume ratio when the frequency is 60 Hz. In addition, the one-point narrative line is a curve showing the relationship between the internal volume and pressure during theoretical thermal compression. In the above-mentioned fixed inner volume ratio, at a frequency of 30 Hz, insufficient compression occurs at a point (A), and the pressure decreases rapidly. In addition, if the frequency is too high and compression occurs at the point (B), the pressure will increase much more than the theoretical value. From the above, it can not be simply applied to the capacity control of an inverter for a screw compressor. However, as in the present embodiment, by setting the variable inner volume ratio, as shown by the solid line, when the inner volume ratio is fixed, the insufficient compression occurring at a frequency of 30 Hz can be avoided, and the pressure can be reduced at the same time. The magnitude of the change. In addition, when the internal volume ratio is fixed, at a frequency of 90 Hz, over-compression can be avoided and the magnitude of pressure fluctuation can be reduced. In addition, in the above-mentioned embodiment, although the case where it is applied to a refrigerator is taken as an example, the capacity and internal valley ratio control system of the variable internal volume ratio type inverter screw compressor will be described. However, the present invention is not limited to this. As long as the detection signals are input to the rotation number output sections 37 and 52 of the control devices 36 and 51 as shown in Figs. 2 and 3, they may be signals indicating the state of the load. [Brief description of the drawings] Figures 1A and 1B are structural diagrams of important parts of the variable internal volume ratio variable frequency screw compressor 88745. 17. 200412397 of the present invention. Fig. 2 is a diagram showing the fb force / inner valley product ratio control system of the variable inner product ratio type variable frequency screw compressor shown in Fig. 丨. FIG. 3 is a diagram showing a capability / content volume ratio control system different from FIG. 2. 〃Figure 4 is a graph showing the relationship between the operating frequency and the compression ratio and the optimum internal volume ratio. Figure 〇 Figure Figure 5% of members are not cold; gold office; t »-. / 、 The relationship between the compression ratios of the compressor efficiency of this force. Figure 6 A, 6B is the relationship between the internal volume and pressure of the screw compressor. Figure 7 is a description of the representative symbols of the variable contents. Stepping motor 2 lever 3 variable VI valve 4 capacity control valve 5 discharge port 7 housing 8 discharge port 9 hydraulic piston 10 control device 11 electric motor 12 mule 13 sectional view of rotor compressor 88745 '18- 200412397 14 main shaft 15 variable frequency Compressor 16, 17 bearing 18 screw rotor 19 slide valve 20 discharge port 21 support plate 22 load 23-connecting plate 24 cylinder 25 piston 26 living base load 27 compression controller 28 fluid control device 31 screw compressor 3 2 condenser 33 expansion Valve 34 Evaporator 35 Temperature sensor 36 Control device 37 Number of revolutions output section 38 Optimum internal volume ratio output section 39 Helical compression section 40 Low-pressure side pressure sensor
88745 19- 200412397 41 高壓側壓力感應器 5 1 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 -20-88745 19- 200412397 41 High pressure side pressure sensor 5 1 Control device 52 Number of revolutions output section 53 Optimum internal volume ratio output section 54 Inverter 88745 -20-