TWI494508B - Screw compressor - Google Patents
Screw compressor Download PDFInfo
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- TWI494508B TWI494508B TW100124459A TW100124459A TWI494508B TW I494508 B TWI494508 B TW I494508B TW 100124459 A TW100124459 A TW 100124459A TW 100124459 A TW100124459 A TW 100124459A TW I494508 B TWI494508 B TW I494508B
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- valve body
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- compression
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Classifications
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C18/00—Rotary-piston pumps specially adapted for elastic fluids
- F04C18/08—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing
- F04C18/12—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type
- F04C18/14—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons
- F04C18/16—Rotary-piston pumps specially adapted for elastic fluids of intermeshing-engagement type, i.e. with engagement of co-operating members similar to that of toothed gearing of other than internal-axis type with toothed rotary pistons with helical teeth, e.g. chevron-shaped, screw type
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/12—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves
- F04C28/125—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using sliding valves with sliding valves controlled by the use of fluid other than the working fluid
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/10—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber
- F04C28/16—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by changing the positions of the inlet or outlet openings with respect to the working chamber using lift valves
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C28/00—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids
- F04C28/24—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves
- F04C28/26—Control of, monitoring of, or safety arrangements for, pumps or pumping installations specially adapted for elastic fluids characterised by using valves controlling pressure or flow rate, e.g. discharge valves or unloading valves using bypass channels
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- F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
- F04—POSITIVE - DISPLACEMENT MACHINES FOR LIQUIDS; PUMPS FOR LIQUIDS OR ELASTIC FLUIDS
- F04C—ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT MACHINES FOR LIQUIDS; ROTARY-PISTON, OR OSCILLATING-PISTON, POSITIVE-DISPLACEMENT PUMPS
- F04C2270/00—Control; Monitoring or safety arrangements
- F04C2270/18—Pressure
- F04C2270/185—Controlled or regulated
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- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Physics & Mathematics (AREA)
- Fluid Mechanics (AREA)
- Applications Or Details Of Rotary Compressors (AREA)
Description
本發明是關於一種，適合用於構成空氣調和機、極冷器單元、冷凍機等的冷凍循環的裝置的螺旋壓縮機。The present invention relates to a screw compressor suitable for use in an apparatus for constituting a refrigeration cycle of an air conditioner, a cryogen unit, a refrigerator, and the like.
在空氣調和機或極冷器單元等使用螺旋壓縮機時，由於要在大範圍的吸入壓力或吐出壓力使用，所以螺旋轉子齒溝內的壓力會因為運轉條件可能會變的比吐出壓力更高(以下稱為過壓縮)。於此，提案有減輕過壓縮用的螺旋壓縮機(例如參閱專利文獻1)。When a screw compressor is used in an air conditioner or a cryostat unit, the pressure in the helical rotor groove may be higher than the discharge pressure due to operating conditions due to the use of a wide range of suction pressure or discharge pressure. (hereinafter referred to as over-compression). Here, a screw compressor for reducing over-compression has been proposed (for example, see Patent Document 1).
專利文獻1記載的螺旋壓縮機，是具備有：旋轉軸以大致平行相互咬合的方式一面旋轉的陽轉子(主轉子)及陰轉子(副轉子)；收納該等陽轉子及陰轉子的齒部的內孔，及具有該內孔的轉子軸向吐出側開口的端面的主殼體(殼體)；以及與該主殼體的轉子軸向吐出側連接的吐出殼(殼體壁)。吐出殼具有：抵接在主殼體的端面，覆蓋內孔的開口的吐出側端面；被形成在該吐出側端面的吐出埠(排出窗)；從被形成在陽轉子及陰轉子的齒溝的壓縮作動室經由吐出埠吐出壓縮氣體的吐出室；在吐出側端面的吐出埠的附近，在陽轉子側及陰轉子側之中的至少其中一方，在與轉子旋轉方向相反側的位置開口的閥孔(孔)；以及連通該閥孔與吐出室的旁通流路，並設有開閉閥孔的閥裝置(溢流閥)。The screw compressor disclosed in Patent Document 1 includes a male rotor (main rotor) and a female rotor (sub rotor) in which the rotating shafts rotate in a substantially parallel manner, and the teeth of the male and female rotors are accommodated. The inner hole, and a main casing (housing) having an end surface of the inner hole of the rotor axial discharge side opening; and a discharge casing (housing wall) connected to the rotor axial discharge side of the main casing. The spouting case has a discharge side end surface that abuts against an end surface of the main casing, covers an opening of the inner hole, a discharge port formed on the discharge end surface (discharge window), and a groove formed from the male rotor and the female rotor. At least one of the male rotor side and the female rotor side is opened at a position opposite to the rotor rotation direction in the vicinity of the discharge port on the discharge side end surface in the vicinity of the discharge port on the discharge side end surface. a valve hole (a hole); and a bypass flow path that communicates the valve hole and the discharge chamber, and a valve device (relief valve) that opens and closes the valve hole.
前述閥裝置具有：被配置在閥孔內的閥體；以及朝主殼體側彈推該閥體的彈簧(推壓彈簧)。而且，例如將閥體朝主殼體側移動，並關閉閥孔時，埠從壓縮作動室經由吐出朝吐出室吐出壓縮氣體。另一方面，使閥體移動到與主殼體側的相反側，打開閥孔時，不僅吐出埠，經由閥孔及旁通流路朝吐出室吐出壓縮氣體。藉此，減輕過壓縮。The valve device has a valve body disposed in the valve hole, and a spring (pushing spring) that pushes the valve body toward the main housing side. Further, for example, when the valve body is moved toward the main casing side and the valve hole is closed, the compressed gas is discharged from the compression chamber through the discharge to the discharge chamber. On the other hand, when the valve body is moved to the side opposite to the main casing side, when the valve hole is opened, not only the sputum is discharged, but also the compressed gas is discharged to the discharge chamber through the valve hole and the bypass flow path. Thereby, the over-compression is alleviated.
又，作為閥體的制動器，在閥體及閥孔形成有段差部。藉此，例如將閥體朝主殼體側移動時，閥體的前端面相對於吐出殼的端面成為同一面，而構成防止閥體與轉子的齒部端面接觸的情況。Further, as the brake of the valve body, a step portion is formed in the valve body and the valve hole. Thereby, for example, when the valve body is moved toward the main casing side, the front end surface of the valve body is flush with the end surface of the discharge casing, and the valve body is prevented from coming into contact with the end surface of the tooth portion of the rotor.
[專利文獻1]日本特開昭61-79886號公報[Patent Document 1] Japanese Patent Laid-Open No. 61-79886
然而，已知上述先前技術中，有以下必須改善的課題。However, it is known that the above prior art has the following problems that must be improved.
亦即，上述先前技術中，由於來自壓縮作動室的壓力作用在前述閥體，所以壓縮作動室成為過壓縮的狀態(壓縮作動室的壓力＞吐出室的壓力(吐出壓力))，克服前述彈簧的推壓力時，前述閥體打開。可是，閥體打開時，閥體的壓縮作動室側的壓力馬上與吐出室側的壓力變成一樣。另一方面，前述閥體的反壓，經常成為吐出室的壓力，所以作用在閥體的壓力馬上平衡。因此，藉由朝主殼體側彈推閥體的前述彈簧的作用，前述閥體馬上被關閉。因此，壓縮作動室成為過壓縮狀態時，隨著轉子的旋轉，壓縮作動室每次通過閥體時，形成閥體反覆的開閉，會有閥體敲擊制動器，產生打擊聲或振動的課題。That is, in the above prior art, since the pressure from the compression operation chamber acts on the valve body, the compression operation chamber is in an over-compressed state (pressure of the compression operation chamber > pressure of the discharge chamber (discharge pressure)), overcoming the aforementioned spring When the pressure is pushed, the aforementioned valve body is opened. However, when the valve body is opened, the pressure on the compression chamber side of the valve body immediately becomes the same as the pressure on the discharge chamber side. On the other hand, since the back pressure of the valve body often becomes the pressure of the discharge chamber, the pressure acting on the valve body immediately balances. Therefore, the valve body is immediately closed by the action of the spring that pushes the valve body toward the main casing side. Therefore, when the compression actuating chamber is in the over-compressed state, the valve body is repeatedly opened and closed each time the compression actuating chamber passes through the valve body as the rotor rotates, and the valve body knocks the brake to cause a blow sound or vibration.
本發明的目的在獲得一種，可減低減輕過壓縮的閥體的打擊聲或振動的螺旋壓縮機。SUMMARY OF THE INVENTION An object of the present invention is to provide a screw compressor which can reduce the struck sound or vibration of an over-compressed valve body.
為了達成上述目的，本發明是一種，具有：旋轉軸一面大致平行相互咬合一面旋轉的陽轉子及陰轉子；具有收納前述陽轉子及陰轉子的內孔的主殼體；以及具有與前述主殼體的轉子軸向吐出側連接，並抵接在前述主殼體的端面，覆蓋前述內孔開口的吐出側端面的吐出殼，且具備有：由前述陽轉子及陰轉子所形成的壓縮作動室，經由被形成在前述主殼體或前述吐出殼的至少任一殼體的吐出埠，吐出壓縮氣體吐出室或吐出流路；在前述吐出埠附近，且位在前述陽轉子或陰轉子的至少一方側的前述吐出殼的吐出側端面，被形成在前述壓縮作動室開口的位置的閥孔；連通該閥孔與前述吐出室或吐出流路的旁通流路；以及被配置在前述閥孔內的閥體之螺旋壓縮機，其特徵為：具備有：使前述閥體打開關閉用的閥體驅動裝置；以及檢知在前述壓縮作動室是否有過壓縮發生，當檢知有過壓縮發生時，控制前述閥體驅動裝置，打開前述閥體的控制裝置，前述控制裝置，是依據吸入到壓縮機的吸入壓力與壓縮機的吐出壓力，求取運轉中的壓力比，並將該壓力比與預先被記憶的所設定的壓力比進行比較，當運轉中的壓力比變的比前述所設定的壓力比更小時，判斷有過壓縮發生，進而控制前述閥體驅動裝置，打開前述閥體，前述閥體驅動裝置具備有：被設在前述閥體的背面側的汽缸、在該汽缸 內往復動的活塞、以及連接該活塞與前述閥體的推桿，當過壓縮發生時，使壓力作用在前述活塞，而構成打開前述閥體，在前述活塞的閥體側的汽缸內設置朝反閥體側推壓前述活塞的彈簧，而構成在前述活塞的反閥體側的汽缸內引導壓縮機吐出側的壓縮氣體，當沒有過壓縮發生的狀態時，關閉前述閥體，在過壓縮發生時，藉由對前述活塞的閥體側的汽缸內賦予壓縮機吐出側的壓力，使前述活塞朝反閥體側移動，打開前述閥體。In order to achieve the above object, the present invention is directed to a male rotor and a female rotor in which a rotating shaft rotates while being substantially parallel to each other, a main casing having an inner hole for accommodating the male rotor and the female rotor, and a main casing The rotor of the body is connected to the axial discharge side, and abuts against the end surface of the main casing, covers the discharge casing of the discharge end surface of the opening of the inner hole, and includes a compression chamber formed by the male rotor and the female rotor. Discharging a compressed gas discharge chamber or a discharge flow path through a discharge port formed in at least one of the main casing or the discharge case; and at least in the vicinity of the discharge port and at least the male rotor or the female rotor a discharge side end surface of the discharge case on one side is formed in a valve hole at a position where the compression operation chamber is opened, a bypass flow path that communicates the valve hole with the discharge chamber or the discharge flow path, and a valve hole that is disposed in the valve hole The screw compressor of the valve body is characterized in that: a valve body driving device for opening and closing the valve body is provided; and detecting whether or not the compression operating chamber is present Compression occurs, and when it is detected that compression has occurred, the valve body driving device is controlled to open the control device for the valve body, and the control device is operated according to the suction pressure drawn into the compressor and the discharge pressure of the compressor. The pressure ratio in the middle, and comparing the pressure ratio with the set pressure ratio previously stored, and when the pressure ratio during operation is smaller than the set pressure ratio, it is judged that over-compression occurs, thereby controlling the foregoing The valve body driving device opens the valve body, and the valve body driving device includes a cylinder provided on a back side of the valve body, and the cylinder a reciprocating piston and a push rod connecting the piston and the valve body, when over-compression occurs, a pressure is applied to the piston, and the valve body is opened to be disposed in a cylinder on a valve body side of the piston The valve body side pushes the spring of the piston, and the compressed gas that guides the discharge side of the compressor is guided in the cylinder on the valve body side of the piston. When there is no over-compression, the valve body is closed and over-compressed. At the time of occurrence, the piston is moved toward the counter valve body side by the pressure on the compressor discharge side in the cylinder side of the valve body side of the piston, and the valve body is opened.
根據本發明可獲得一種，可減低減輕過壓縮的閥體的打擊聲或振動之螺旋壓縮機。According to the present invention, a screw compressor capable of reducing the struck sound or vibration of an over-compressed valve body can be obtained.
以下，依據圖面說明本發明的實施例。Hereinafter, embodiments of the present invention will be described in accordance with the drawings.
使用圖1~圖8說明本發明的螺旋壓縮機的實施例1。Embodiment 1 of the screw compressor of the present invention will be described with reference to Figs. 1 to 8 .
圖1表示本發明的螺旋壓縮機的實施例1的縱剖視圖，圖2為圖1的右側視圖，圖3為圖1的III-III箭頭視剖視圖(表示吐出殼的吐出側端面的圖，並以兩點鏈線表示主殼體的端面的內孔的位置)，圖4為圖1的IV-IV箭頭視剖視圖(表示主殼體的端面的圖，並以兩點鏈線表示吐出殼的吐出側端面的閥孔的位置)，圖5是說明本發明的實施例1的壓縮作動室、吐出埠、閥孔及旁通流路的位置關係的圖。1 is a longitudinal cross-sectional view of a first embodiment of a screw compressor according to the present invention, FIG. 2 is a right side view of FIG. 1, and FIG. 3 is a cross-sectional view taken along the line III-III of FIG. 1 (a view showing a discharge side end surface of the discharge case, and FIG. 4 is a cross-sectional view taken along line IV-IV of FIG. 1 (a view showing an end surface of the main casing, and showing the discharge shell with a two-dot chain line). FIG. 5 is a view for explaining the positional relationship between the compression operation chamber, the discharge port, the valve hole, and the bypass flow path in the first embodiment of the present invention.
在圖1，螺旋壓縮機具備有：壓縮機本體1；驅動該壓縮機本體1的馬達(電動機)2；以及收納該馬達2的馬達殼體13。馬達殼體13是在馬達2的反壓縮機本體側形成吸入室(低壓室)5，並形成氣體從吸入口6經過篩濾網7流入前述吸入室5內。前述馬達2是由：被安裝在旋轉軸10的轉子11；以及被配設在該轉子11的外周側的定子12所構成，前述定子被固定在前述馬達殼體13的內面。In FIG. 1, a screw compressor includes a compressor main body 1, a motor (electric motor) 2 that drives the compressor main body 1, and a motor housing 13 that houses the motor 2. The motor casing 13 forms a suction chamber (low pressure chamber) 5 on the counter compressor main body side of the motor 2, and forms a gas flowing from the suction port 6 through the screen 7 into the suction chamber 5. The motor 2 is composed of a rotor 11 attached to the rotating shaft 10 and a stator 12 disposed on the outer peripheral side of the rotor 11, and the stator is fixed to the inner surface of the motor casing 13.
前述壓縮機本體1是具備有：與前述馬達殼體13連接，內建有螺旋轉子14的主殼體15；以及與該主殼體15的吐出側連接的吐出殼16。The compressor main body 1 is provided with a main casing 15 that is connected to the motor casing 13 and has a spiral rotor 14 built therein, and a discharge casing 16 that is connected to the discharge side of the main casing 15.
在前述主殼體15形成有收容前述螺旋轉子14的齒部的圓筒狀的內孔20，該內孔20的轉子軸向吐出側為開口。在形成該開口的前述主殼體15的端面21側形成有徑方向的吐出埠23，且也形成有與該吐出埠23連接的吐出流路90。A cylindrical inner hole 20 for accommodating the tooth portion of the spiral rotor 14 is formed in the main casing 15, and the rotor axial discharge side of the inner hole 20 is an opening. A discharge port 23 in the radial direction is formed on the end surface 21 side of the main casing 15 that forms the opening, and a discharge flow path 90 connected to the discharge port 23 is also formed.
如圖4所示，前述螺旋轉子14是由旋轉軸以平行相互咬合的方式一面旋轉的陽轉子14A及陰轉子14B所構成。又，前述內孔20是由：收容陽轉子的內孔20A與收容陰轉子的內孔20B所構成，前述吐出埠23也是由：陽轉子側的吐出埠23A與陰轉子側的吐出埠23B所構成。As shown in Fig. 4, the spiral rotor 14 is composed of a male rotor 14A and a female rotor 14B that rotate while rotating the shafts in parallel. Further, the inner hole 20 is composed of an inner hole 20A for accommodating the male rotor and an inner hole 20B for accommodating the female rotor, and the discharge port 23 is also provided by the discharge port 23A on the male rotor side and the discharge port 23B on the female rotor side. Composition.
前述主殼體15的轉子軸向吸入側(圖1的左側)是與前述馬達殼體13連接，該馬達殼體13內部的前述轉子11與定子12之間的間隙等，是形成使前述吸入室5與前述壓縮機本體1連通的吸入通路所構成。The rotor axial suction side (the left side in FIG. 1) of the main casing 15 is connected to the motor casing 13, and a gap or the like between the rotor 11 and the stator 12 inside the motor casing 13 is formed to allow the aforementioned suction. The chamber 5 is formed by a suction passage that communicates with the compressor body 1.
在前述陽轉子14A及陰轉子14B的齒溝，是如圖4所示，形成有壓縮作動室36A、36B，該壓縮作動室是與螺旋轉子的旋轉一起依序改變成與形成在主殼體15的吸入側(馬達殼體13側)的吸入埠22連通的吸氣行程的壓縮作動室；壓縮被吸氣的氣體的壓縮行程的壓縮作動室；以及與前述吐出埠23、25連通，吐出壓縮後的氣體的吐出行程的壓縮作動室。前述吐出埠23A、23B相對於吐出行程的壓縮作動室被形成在陽轉子或陰轉子的徑方向外側(圖1的上側)。In the tooth grooves of the male rotor 14A and the female rotor 14B, as shown in FIG. 4, compression operating chambers 36A, 36B are formed, which are sequentially changed and formed in the main casing together with the rotation of the spiral rotor. a compression operation chamber for an intake stroke in which the suction port 22 of the suction side (the motor casing 13 side) communicates with the compressor; a compression operation chamber that compresses a compression stroke of the inhaled gas; and a communication chamber that communicates with the discharge ports 23 and 25, and discharges The compression chamber of the discharge stroke of the compressed gas. The compression chambers of the discharge ports 23A and 23B with respect to the discharge stroke are formed on the outer side in the radial direction of the male rotor or the female rotor (upper side in FIG. 1).
如圖1、圖3所示，在前述吐出殼16的吐出側端面24形成有軸向的吐出埠25與吐出室26。亦即，吐出殼16具有：抵接在主殼體15的端面21，覆蓋前述內孔20A、20B的開口的吐出側端面24；被形成在該吐出側端面24的陽轉子側的吐出埠25A及陰轉子側的吐出埠25B；以及從前述壓縮作動室經由前述吐出埠23A、23B、25A、25B被吐出的壓縮氣體流入的吐出室26。As shown in FIGS. 1 and 3, an axial discharge spout 25 and a discharge chamber 26 are formed on the discharge-side end surface 24 of the discharge casing 16. In other words, the discharge case 16 has a discharge-side end surface 24 that abuts against the end surface 21 of the main casing 15, covers the opening of the inner holes 20A and 20B, and a discharge port 25A that is formed on the male-rotor side of the discharge-side end surface 24. And a discharge port 25B on the female rotor side; and a discharge chamber 26 into which the compressed gas discharged from the compression operation chamber through the discharge ports 23A, 23B, 25A, and 25B flows.
如圖1所示，前述陽轉子14A的吸入側軸部，是由配設在前述主殼體15的滾動軸承17及配設在馬達殼體13的滾珠軸承91所支撐，前述陽轉子14A的吐出側軸部，是由被配設在吐出殼16的滾動軸承18及滾珠軸承19所支撐。又，前述陰轉子14B的吸入側軸部，是由被配設在前述主殼體15的滾動軸承(未圖示)所支撐，前述陰轉子14B的吐出側軸部，是由被配設在吐出殼16的滾動軸承及滾珠軸承(未圖示)所支撐。陽轉子14A的前述吸入側軸部是與馬達2的旋轉軸10直接連結，藉由馬達2的驅動，陽轉子14A旋轉，隨著該旋轉，前述陰轉子14B一面與陽轉子14A咬合一面旋轉。As shown in Fig. 1, the suction-side shaft portion of the male rotor 14A is supported by a rolling bearing 17 disposed in the main casing 15 and a ball bearing 91 disposed in the motor casing 13, and the male rotor 14A is discharged. The side shaft portion is supported by the rolling bearing 18 and the ball bearing 19 disposed in the discharge casing 16. Further, the suction-side shaft portion of the female rotor 14B is supported by a rolling bearing (not shown) disposed in the main casing 15, and the discharge-side shaft portion of the female rotor 14B is disposed to be discharged. The rolling bearing of the casing 16 and the ball bearing (not shown) are supported. The suction-side shaft portion of the male rotor 14A is directly coupled to the rotating shaft 10 of the motor 2, and the male rotor 14A is rotated by the driving of the motor 2. With this rotation, the female rotor 14B rotates while being engaged with the male rotor 14A.
在前述螺旋轉子14被壓縮的氣體，從前述吐出埠23、25流出到前述吐出室26或前述吐出流路90內，從該吐出通路90流到設在主殼體15的吐出口9，經由與該吐出口9連接的吐出配管94被送到油分離器92。在該油分離機92，分離在壓縮機本體1內被壓縮的氣體與被混入在該氣體的油。在油分離機92被分離的油，是經由油返回管93回到被設在前述壓縮機本體1下部的油槽95，被積存在這裡之後，為了潤滑支撐螺旋轉子14的軸部或馬達2的旋轉軸10的前述軸承17、18、19、91，再次被供給到該等的軸承。另一方面，在油分離機92被分離油的高壓氣體，是經由配管96供給到外部(例如構成冷凍循環的冷凝器)。The gas compressed by the spiral rotor 14 flows out from the discharge ports 23 and 25 into the discharge chamber 26 or the discharge flow path 90, and flows from the discharge passage 90 to the discharge port 9 provided in the main casing 15, via The discharge pipe 94 connected to the discharge port 9 is sent to the oil separator 92. In the oil separator 92, the gas compressed in the compressor main body 1 and the oil mixed in the gas are separated. The oil separated in the oil separator 92 is returned to the oil groove 95 provided in the lower portion of the compressor main body 1 via the oil return pipe 93, and is accumulated therein to lubricate the shaft portion of the spiral rotor 14 or the motor 2 The aforementioned bearings 17, 18, 19, 91 of the rotary shaft 10 are again supplied to the bearings. On the other hand, the high-pressure gas from which the oil is separated in the oil separator 92 is supplied to the outside via a pipe 96 (for example, a condenser constituting a refrigeration cycle).
從吸入口6被吸入吸入室5的氣體，通過馬達殼體13的內部之際，冷卻轉子11及定子12，之後，經由壓縮機本體1的吸入埠22，流入由前述螺旋轉子14所形成的壓縮作動室，隨著陽轉子14A及陰轉子14B的旋轉，壓縮作動室36A、36B一面朝轉子軸向移動一面縮小容積，氣體進而被壓縮。而構成在壓縮機作動室被壓縮的氣體，經由吐出埠23A、23B、25A、25B及吐出室26流入吐出流路90，並成為從吐出口9送出到吐出配管94。The gas sucked into the suction chamber 5 from the suction port 6 passes through the inside of the motor casing 13, and cools the rotor 11 and the stator 12, and then flows into the spiral rotor 14 through the suction port 22 of the compressor main body 1. In the compression operation chamber, as the male rotor 14A and the female rotor 14B rotate, the compression actuating chambers 36A and 36B move toward the rotor in the axial direction to reduce the volume, and the gas is further compressed. The gas that is compressed in the compressor operation chamber flows into the discharge flow path 90 through the discharge ports 23A, 23B, 25A, and 25B and the discharge chamber 26, and is sent out from the discharge port 9 to the discharge pipe 94.
如圖3所示，在前述吐出殼16形成有：在其吐出側端面24的陰轉子14B側的吐出埠25B的附近，在與該陰轉子14B的旋轉方向在相反側(圖3的右側)的位置開口的閥孔(汽缸)28，該閥孔28的略中心是位在前述主殼體15的端面21的陰轉子14B側的內孔20B的開口緣。又，在前述吐出殼16形成有連通閥孔28與吐出室26的旁通溝29，其是比主殼體15的端面21的陰轉子14B側的內孔20B的開口緣更位在轉子徑方向外側，並由該旁通溝29與覆蓋該溝的主殼體15的端面21形成旁通流路。在前述閥孔28設有開閉該閥孔28的閥體31。As shown in Fig. 3, the discharge case 16 is formed in the vicinity of the discharge port 25B on the side of the female rotor 14B on the discharge side end surface 24, on the opposite side to the rotation direction of the female rotor 14B (on the right side in Fig. 3). The valve hole (cylinder) 28 is opened at an approximate position, and the center of the valve hole 28 is an opening edge of the inner hole 20B on the side of the female rotor 14B of the end surface 21 of the main casing 15. Further, the discharge casing 16 is formed with a bypass groove 29 that communicates the valve hole 28 and the discharge chamber 26, which is located more in the rotor diameter than the opening edge of the inner hole 20B on the female rotor 14B side of the end surface 21 of the main casing 15. The bypass flow path is formed by the bypass groove 29 and the end surface 21 of the main casing 15 covering the groove. The valve body 31 is provided with a valve body 31 that opens and closes the valve hole 28.
接著，依據圖6～圖8，針對驅動前述閥體31用的閥體驅動裝置進行說明。Next, a valve body driving device for driving the valve body 31 will be described with reference to Figs. 6 to 8 .
圖6及圖7是圖2的VI-VI線箭頭視剖視圖，且是說明驅動前述閥體31的閥體驅動裝置的構造的圖，圖6表示閥體31的關閉狀態的圖，圖7表示閥體31的打開狀態的圖。圖8為圖6的VIII-VIII線箭頭視剖視圖。6 and FIG. 7 are cross-sectional views taken along the line VI-VI of FIG. 2, and are views showing a structure of a valve body driving device that drives the valve body 31, and FIG. 6 is a view showing a closed state of the valve body 31, and FIG. A diagram of the open state of the valve body 31. Fig. 8 is a cross-sectional view taken along the line VIII-VIII of Fig. 6;
圖6及圖7中，閥體驅動裝置30是具備有：在可滑動地被設在前述閥孔28內的閥體31的背面側(圖6的右側)連接有一端側的推桿53、經由螺拴52與該推桿53的另一他端側連接的活塞51、可滑動地收納該活塞51的汽缸35。前述汽缸35被形成在吐出殼16，在該吐出殼16也設有滑動自如地支撐前述推桿53的桿孔101。在前述桿孔101設有密封環50，密封汽缸35的汽缸室內與閥體31的反壓室28a之間。又，在前述反壓室28a，經由被形成在吐出殼16的連通孔102導入壓縮機吐出側的壓力。亦即，如圖6及圖8所示，前述連通孔102的一端側，在前述反壓室28a開口，前述連通孔102的另一他端側與前述吐出室26(參閱圖3)連通。In FIG. 6 and FIG. 7 , the valve body driving device 30 is provided with a push rod 53 that is connected to one end side on the back side (the right side in FIG. 6 ) of the valve body 31 that is slidably provided in the valve hole 28 , A piston 51 connected to the other end side of the push rod 53 via a bolt 52 slidably houses the cylinder 35 of the piston 51. The cylinder 35 is formed in the discharge casing 16, and the discharge casing 16 is also provided with a rod hole 101 that slidably supports the push rod 53. A seal ring 50 is provided in the rod hole 101 to seal between the cylinder chamber of the cylinder 35 and the counter pressure chamber 28a of the valve body 31. Further, the pressure in the counter-pressure chamber 28a is introduced into the compressor discharge side via the communication hole 102 formed in the discharge casing 16. That is, as shown in FIGS. 6 and 8, one end side of the communication hole 102 is opened in the back pressure chamber 28a, and the other end side of the communication hole 102 communicates with the discharge chamber 26 (see FIG. 3).
在前述活塞51的外周安裝有防止被形成在該活塞51的兩側的汽缸室35A、35B間洩漏用的密封環54。又，在前述汽缸室35A(反閥體側的汽缸35內)，連通孔32的一端側在前述活塞51的移動範圍外的部分(汽缸室35A的右端側)開口，該連通孔32的另一他端側，是如圖8所示在前述吐出室26開口。亦即，汽缸室35A是經由前述連通孔32與前述吐出室26(參閱圖3)連通，並構成壓縮機吐出側的壓力經常被導入前述汽缸室35A。A seal ring 54 for preventing leakage between the cylinder chambers 35A and 35B formed on both sides of the piston 51 is attached to the outer circumference of the piston 51. Further, in the cylinder chamber 35A (in the cylinder 35 on the valve body side), one end side of the communication hole 32 is opened at a portion outside the range of movement of the piston 51 (the right end side of the cylinder chamber 35A), and the other of the communication holes 32 On the other end side, it is opened in the aforementioned discharge chamber 26 as shown in FIG. That is, the cylinder chamber 35A communicates with the discharge chamber 26 (see FIG. 3) via the communication hole 32, and the pressure constituting the compressor discharge side is often introduced into the cylinder chamber 35A.
在前述汽缸室35B(閥體側的汽缸內)，如圖6及圖7所示，連通孔34的一端在活塞51的移動範圍外的部分(汽缸室35B的左端側)開口，該連通孔34的另一他端側經由毛細管120，如圖2所示與油槽95連通，而形成油壓供給路。又，前述連通孔34是構成經由連通路(油壓排出路)80，也與低壓空間(在圖6為吸入埠22)連通，在其連通路80的途中設有開閉該連通路80用的電磁閥42。藉由如此的構成，形成可藉由前述電磁閥42的開閉，一邊將油槽95的高壓油導入汽缸室35B，一邊經由連通路80及電磁閥42朝吸入埠22側排出汽缸室35B的油。又，在前述汽缸室35B設置朝端蓋60側(在反閥體31側是在圖6的右側)彈推前述活塞51的彈簧33。In the cylinder chamber 35B (in the cylinder on the valve body side), as shown in FIGS. 6 and 7, one end of the communication hole 34 is opened at a portion outside the range of movement of the piston 51 (the left end side of the cylinder chamber 35B), and the communication hole is opened. The other end side of the 34 is connected to the oil groove 95 via the capillary 120 as shown in Fig. 2 to form a hydraulic supply path. Further, the communication hole 34 is configured to communicate with the low-pressure space (intake port 22 in FIG. 6) via the communication passage (hydraulic discharge passage) 80, and is provided to open and close the communication passage 80 in the middle of the communication passage 80. Solenoid valve 42. With such a configuration, the oil of the cylinder chamber 35B is discharged to the suction port 22 side via the communication passage 80 and the electromagnetic valve 42 while the high pressure oil of the oil groove 95 is introduced into the cylinder chamber 35B by the opening and closing of the electromagnetic valve 42. Further, the cylinder chamber 35B is provided with a spring 33 that pushes the piston 51 toward the end cover 60 side (on the reverse side of the valve body 31 side).
前述閥體31雖是在前述壓縮作動室36A、36B，沒有過壓縮產生的情況，被控制成關閉狀態，可是關閉閥體31時，控制使開前述電磁閥42成為打開狀態。藉此，汽缸室35B經由連通孔34及連通路80與吸入埠22側連通而成為低壓。另一方面，在汽缸室35A，壓縮機吐出側的氣體壓常時作用。因此，如圖6所示，活塞51克服彈簧33的推壓力朝主殼體15側移動，閥體31被推到前述主殼體15的端面21，閥孔28因而被關閉。The valve body 31 is controlled to be in a closed state without being over-compressed in the compression operating chambers 36A and 36B. However, when the valve body 31 is closed, the solenoid valve 42 is opened to be opened. Thereby, the cylinder chamber 35B communicates with the suction port 22 side via the communication hole 34 and the communication path 80, and becomes a low pressure. On the other hand, in the cylinder chamber 35A, the gas pressure on the discharge side of the compressor acts constantly. Therefore, as shown in Fig. 6, the piston 51 is moved toward the main casing 15 side against the urging force of the spring 33, and the valve body 31 is pushed to the end surface 21 of the aforementioned main casing 15, and the valve hole 28 is thus closed.
此外，前述毛細管120的前述連通孔34側雖也與前述吸入埠22連通，可是，由於經由前述毛細管120油的流動被壓縮，所以從油槽95被排出到吸入埠22的油的量可以降到最少的量，並可降低因前述油造成來到壓縮機的吸入氣體(例如冷媒氣體)過熱的情形，並進依不抑制體積效率的降低。又，在本實施例，由於是形成朝吸入埠22排出前述油，所以因前述油造成被吸入壓縮機的冷媒氣體過熱的時間也可極為縮小，由這一點，由於也可減少因前述油加熱冷媒氣體的情形，所以可抑制體積效率的降低。Further, the communication hole 34 side of the capillary tube 120 is also in communication with the suction port 22, but since the flow of the oil through the capillary tube 120 is compressed, the amount of oil discharged from the oil groove 95 to the suction port 22 can be reduced to The minimum amount can reduce the overheating of the suction gas (for example, refrigerant gas) coming to the compressor due to the aforementioned oil, and does not inhibit the decrease in volumetric efficiency. Further, in the present embodiment, since the oil is discharged to the suction port 22, the time during which the refrigerant gas sucked into the compressor is overheated by the oil can be extremely reduced, and the oil heating can be reduced. In the case of a refrigerant gas, it is possible to suppress a decrease in volumetric efficiency.
過壓縮在前述壓縮作動室36A、36B發生時，前述閥體31被控制成打開。此時，設成關閉前述電磁閥42的狀態，油槽95的高壓油被導入汽缸室35B。亦即，藉由關閉電磁閥42，油槽95的高壓油經由毛細管120被導入汽缸室35B，汽缸室35B的壓力幾乎成為吐出壓力。因此，作用在活塞51的壓力，由於在汽缸室35A側、在汽缸室35B側也幾乎成為相同，所以只有被設在汽缸室35B內的彈簧33所為的推壓力量，使朝向反閥體側(端蓋60側)推壓前述活塞51的力量變大。因此，如圖7所示，活塞51朝端蓋60側移動，閥體31從前述主殼體15分離，前述閥孔28被打開。Over-compression When the aforementioned compression-actuating chambers 36A, 36B occur, the valve body 31 is controlled to open. At this time, the state in which the electromagnetic valve 42 is closed is set, and the high-pressure oil of the oil groove 95 is introduced into the cylinder chamber 35B. That is, by closing the electromagnetic valve 42, the high-pressure oil of the oil groove 95 is introduced into the cylinder chamber 35B via the capillary 120, and the pressure of the cylinder chamber 35B is almost the discharge pressure. Therefore, since the pressure acting on the piston 51 is almost the same on the cylinder chamber 35A side and the cylinder chamber 35B side, only the amount of pressing force by the spring 33 provided in the cylinder chamber 35B is directed toward the valve body side. The force of pushing the aforementioned piston 51 on the side of the end cover 60 becomes large. Therefore, as shown in Fig. 7, the piston 51 moves toward the end cover 60 side, the valve body 31 is separated from the main casing 15, and the valve hole 28 is opened.
開閉閥體31的閥體驅動裝置30雖是成為以上說明的構成，可是在本實施例，進一歩具備有：檢知在前述壓縮作動室36A、36B內是否有過壓縮發生，當檢知有過壓縮的發生時，控制前述閥體驅動裝置30打開前述閥體31的控制裝置，以下依據圖1說明該裝置。The valve body driving device 30 that opens and closes the valve body 31 has the above-described configuration. However, in the present embodiment, it is further provided that it is detected whether or not excessive compression occurs in the compression operating chambers 36A and 36B. When the over-compression occurs, the control device for opening the valve body 31 by the valve body driving device 30 is controlled, and the device will be described below with reference to Fig. 1 .
圖1中，110是檢出從吸入口6被吸入的氣體的壓力的吸入壓力感測器、111是檢出從壓縮機本體1被吐出的壓縮氣體的壓力的吐出壓力感測器，來自該等的壓力感測器110、111的訊號被送到控制裝置112。在控制裝置112，依據來自前述壓力感測器110、111的訊號，計算在這個時點的運轉中的壓力比(吐出壓/吸入壓)。又，在前述控制裝置112記憶有預先被設定的壓力比，並與前述被計算的運轉中的壓力比進行比較。In FIG. 1, reference numeral 110 denotes a suction pressure sensor that detects the pressure of the gas sucked from the suction port 6, and 111 denotes a discharge pressure sensor that detects the pressure of the compressed gas discharged from the compressor main body 1, from which The signals of the pressure sensors 110, 111 are sent to the control device 112. At the control device 112, the pressure ratio (discharge pressure/suction pressure) during the operation at this time point is calculated based on the signals from the pressure sensors 110, 111. Further, the control device 112 stores a pressure ratio set in advance and compares it with the calculated pressure ratio during the operation.
該比較的結果，相對於預先所設定的壓力比，被計算的運轉中的壓力比相同或高的時候，判斷在壓縮作動室36A、36B沒有過壓縮發生，進行藉由將電磁閥42設成開狀態，閥體31朝主殼體15側並被推壓而進關閉閥孔28的控制。As a result of the comparison, when the calculated pressure ratio during operation is the same or higher than the previously set pressure ratio, it is judged that the compression operation chambers 36A and 36B are not over-compressed, and the solenoid valve 42 is set to In the open state, the valve body 31 is pressed toward the main casing 15 side and is controlled to close the valve hole 28.
另一方面，相對於預先所設定的壓力比，被計算的運轉中的壓力比低的時候，判斷過壓縮在壓縮作動室36A、36B發生，進行藉由將電磁閥42設定成閉狀態，使閥體31朝向與主殼體15相反側(圖6的右側)移動，進而打開閥孔28的控制。藉此，由於從壓縮作動室36A、36B經由閥孔28及旁通流路(旁通溝29)朝吐出室26吐出壓縮氣體，所以壓縮作動室的壓力幾乎降低到成為吐出室26的壓力。因此，可減輕過壓縮，並可抑制無謂的動力的消耗。On the other hand, when the calculated pressure ratio during operation is lower than the previously set pressure ratio, it is judged that over-compression is generated in the compression operation chambers 36A and 36B, and the electromagnetic valve 42 is set to the closed state. The valve body 31 is moved toward the opposite side (the right side of FIG. 6) from the main casing 15, thereby opening the control of the valve hole 28. As a result, since the compressed gas is discharged from the compression operation chambers 36A and 36B through the valve hole 28 and the bypass flow path (the bypass groove 29) toward the discharge chamber 26, the pressure in the compression operation chamber is almost lowered to the pressure in the discharge chamber 26. Therefore, over-compression can be alleviated, and unnecessary power consumption can be suppressed.
此外，在本實施例，作為吸入關閉時的壓縮作動室的容積Vs與由閥孔28開始吐出時的壓縮作動室的容積Vd的比的設定容積比Vs/Vd是構成在1.5～3.0的範圍內。Further, in the present embodiment, the set volume ratio Vs/Vd which is a ratio of the volume Vs of the compression operation chamber at the time of suction closing to the volume Vd of the compression operation chamber when the valve hole 28 starts to be discharged is in the range of 1.5 to 3.0. Inside.
又，在本實施例，吐出殼16的吐出側端面24的前述閥孔28，其略中心是構成位在主殼體15的端面21的內孔20B的開口緣的位置。亦即，前述閥孔28是如圖3所示，比內孔20B的開口緣，位在轉子徑方向內側的內側區域在壓縮作動室36B開口，所以，可將其開口面積設大，另一方面，以主殼體15的端面21覆蓋比內孔20B的開口緣更位於轉子徑方向外側的外側區域。藉此，可以覆蓋閥孔28的外側區域的主殼體15的端面21作為閥體31的制動器發揮功能。(亦即，閥體31抵接前述端面21可防止傾斜。)因此，如習知，與在閥體及閥孔形成段差部的構成作為定位閥體用的制動器的時候相比，在本實施例者，可簡化定位閥體用的制動器，由於不用如習知需要高精度的加工，所以可提昇生產性。Further, in the present embodiment, the valve hole 28 of the discharge-side end surface 24 of the discharge casing 16 has a substantially centered position at the opening edge of the inner hole 20B of the end surface 21 of the main casing 15. That is, as shown in FIG. 3, the valve hole 28 is opened at the inner side of the inner side of the rotor in the radial direction of the inner side of the inner side of the rotor 20B, so that the opening area can be increased, and the valve hole 28 can be opened. On the other hand, the end surface 21 of the main casing 15 covers an outer region outside the opening edge of the inner hole 20B in the radial direction of the rotor. Thereby, the end surface 21 of the main casing 15 which can cover the outer region of the valve hole 28 functions as a brake of the valve body 31. (That is, the valve body 31 abuts against the end surface 21 to prevent tilting.) Therefore, as in the prior art, compared with the case where the valve body and the valve hole form a stepped portion as a brake for positioning the valve body, in this embodiment, For example, the brake for positioning the valve body can be simplified, and productivity can be improved because high-precision machining is not required as is conventional.
又，例如與閥孔28的略中心比內孔20B的開口緣更位在轉子徑方向內側的情形相比，可在轉子徑方向外側配置閥體驅動裝置30，故可避免被設在支撐陰轉子14B的吐出側軸部用的吐出殼16的滾動軸承18及滾珠軸承19的相互干涉。因此，由於不用將螺旋轉子14的吐出側軸部做長，所以也可抑制壓縮機的大型化。Further, for example, the valve body driving device 30 can be disposed on the outer side in the radial direction of the rotor as compared with the case where the center of the inner hole 20B is located on the inner side in the radial direction of the rotor hole 28, so that it can be prevented from being placed on the support side. The rolling bearing 18 and the ball bearing 19 of the discharge case 16 for the discharge-side shaft portion of the rotor 14B interfere with each other. Therefore, since it is not necessary to lengthen the discharge-side shaft portion of the spiral rotor 14, it is possible to suppress an increase in size of the compressor.
再者，在本實施例，由於前述旁通流路是由：被形成在吐出殼16的吐出側端面24的旁通溝29與覆蓋該溝的主殼體15的端面21所構成，所以可在鑄造的階段成形旁通溝29，例如與加工形成作為旁通流路旁通孔的情況相比，可減低加工時數。Further, in the present embodiment, the bypass flow path is constituted by the bypass groove 29 formed on the discharge side end surface 24 of the discharge case 16 and the end surface 21 of the main casing 15 covering the groove. The formation of the bypass groove 29 at the stage of casting can reduce the number of machining hours as compared with the case of forming a bypass passage as a bypass flow path.
接著，說明上述的實施例1的變形例。上述實施例1中，如圖3所示，雖針對在吐出殼16的吐出側端面24的陰轉子14B側設置1個閥孔28的例子作了說明，可是，設置上述閥孔的個數或位置並不限於此，例如也可如以下說明的圖9～圖11所示的變形例1～3的構成。Next, a modification of the above-described first embodiment will be described. In the first embodiment, as shown in FIG. 3, an example in which one valve hole 28 is provided on the female rotor 14B side of the discharge-side end surface 24 of the discharge casing 16 is described. However, the number of the valve holes or the number of the valve holes may be provided. The position is not limited thereto, and for example, the configurations of the modifications 1 to 3 shown in FIGS. 9 to 11 described below may be employed.
圖9表示變形例1，此例是只有在吐出殼16的吐出側端面24的陽轉子14A側設置1個閥孔37者。亦即，在吐出殼16的吐出側端面24的陽轉子14A側的吐出埠25A的附近，在與陽轉子14A的旋轉方向相反側開口的位置設置閥孔37者。38是連通前述閥孔37與吐出室26的旁通溝。在前述閥孔37，與圖6～圖8所示者同樣，也設有開閉閥體31或該閥體31用的閥體驅動裝置30。又，關於作為吸入關閉時的壓縮作動室的容積Vs與閥孔37所為的吐出開始時的壓縮作動室的容積Vd的比的設定容積比Vs/Vd，也與上述的實施例1同樣在1.5～3.0的範圍內。再者，吐出殼16的吐出側端面24的閥孔37的中心，也與上述的實施例1同樣，構成幾乎位在主殼體15的端面21的內孔20A的開口緣。Fig. 9 shows a first modification. In this example, only one valve hole 37 is provided on the side of the male rotor 14A on the discharge side end surface 24 of the discharge casing 16. In other words, in the vicinity of the discharge port 25A on the side of the male rotor 14A on the discharge side end surface 24 of the discharge case 16, the valve hole 37 is provided at a position that is open on the side opposite to the rotation direction of the male rotor 14A. 38 is a bypass groove that connects the valve hole 37 and the discharge chamber 26. Similarly to those shown in FIGS. 6 to 8, the valve hole 37 is provided with a valve body driving device 30 for opening and closing the valve body 31 or the valve body 31. In addition, the set volume ratio Vs/Vd of the ratio of the volume Vs of the compression operation chamber at the time of suction closing to the volume Vd of the compression operation chamber at the start of discharge of the valve hole 37 is also 1.5 in the same manner as in the above-described first embodiment. Within the range of ~3.0. Further, the center of the valve hole 37 of the discharge-side end surface 24 of the discharge casing 16 is also configured to have an opening edge of the inner hole 20A almost at the end surface 21 of the main casing 15, similarly to the above-described first embodiment.
因此，即使是圖9所示的變形例1，也可獲得與上述實施例1幾乎同樣的效果。Therefore, even in the first modification shown in Fig. 9, almost the same effects as those of the first embodiment described above can be obtained.
圖10表示變形例2的圖，該例是在吐出殼16的吐出側端面24的陽轉子14A側及陰轉子14B側的兩方分別個設置1個閥孔28或37。亦即，在前述吐出殼16的陰轉子14B側，是與圖3所示者同樣設有閥孔28、旁通溝29及閥體驅動裝置30等，在前述吐出殼16的陽轉子14A側也與圖9所示者同樣，設有閥孔37、旁通溝38及閥體驅動裝置等。此外，該例中，在閥孔28側與閥孔37側，作為吸入被關著時的壓縮作動室的容積Vs與各閥孔所為之吐出開始時的壓縮作動室的容積Vd的比的設定容積比Vs/Vd也可構成彼此相同，也可構成彼此不同。FIG. 10 is a view showing a modification 2 in which one valve hole 28 or 37 is provided in each of the male rotor 14A side and the female rotor 14B side of the discharge side end surface 24 of the discharge casing 16 . In other words, on the side of the female rotor 14B of the discharge casing 16, a valve hole 28, a bypass groove 29, a valve body driving device 30, and the like are provided in the same manner as those shown in Fig. 3, and the male rotor 14A side of the discharge casing 16 is provided. Similarly to the case shown in Fig. 9, a valve hole 37, a bypass groove 38, a valve body driving device, and the like are provided. In this example, the ratio of the volume Vs of the compression operation chamber when the suction is closed to the volume Vd of the compression operation chamber at the start of discharge of each valve hole on the valve hole 28 side and the valve hole 37 side is set. The volume ratios Vs/Vd may also be identical to each other or different from each other.
在該變形例2，也可獲得與上述實施例同樣的效果，並且由於在陽轉子14A側及陰轉子14B側的兩方分別設置閥孔28或37，所以過壓縮時，可從壓縮作動室以更快的速度朝吐出側排出被過壓縮的氣體，可防止過壓縮並抑制多餘的動力的消耗。Also in the second modification, the same effects as those of the above-described embodiment can be obtained, and since the valve holes 28 or 37 are provided on both the side of the male rotor 14A and the side of the female rotor 14B, the compression operation chamber can be obtained from the compression. Exhausting the compressed gas toward the discharge side at a faster rate prevents over-compression and suppresses excessive power consumption.
圖11表示變形例3的圖。上述的各例子中，說明在陰轉子14B側或陽轉子14A側設置1個閥孔28或38，或是在陰轉子14B側及陽轉子14A側的兩方分別設置1個閥孔28或38。而相對於此，該變形例3，是在陰轉子14B側或陽轉子14A側的任一方設置複數個閥孔，或在兩方分別設置複數個閥孔者。例如如圖11所示，在吐出殼16，在陰轉子14B側設置兩個閥孔28A、28B，並且形成連通該等閥孔28A、28B與吐出室26的旁通溝29A。與前述實施例同樣，在前述各閥孔28A、28B分別設置閥體，並且也設置分別打開關閉該等的閥體的閥體驅動裝置。Fig. 11 is a view showing a modification 3. In each of the above-described examples, one valve hole 28 or 38 is provided on the female rotor 14B side or the male rotor 14A side, or one valve hole 28 or 38 is provided on each of the female rotor 14B side and the male rotor 14A side. . On the other hand, in the third modification, a plurality of valve holes are provided on either the female rotor 14B side or the male rotor 14A side, or a plurality of valve holes are provided in each of the two. For example, as shown in Fig. 11, in the discharge casing 16, two valve holes 28A, 28B are provided on the female rotor 14B side, and a bypass groove 29A that communicates the valve holes 28A, 28B and the discharge chamber 26 is formed. Similarly to the above-described embodiment, a valve body is provided in each of the valve holes 28A and 28B, and a valve body driving device that opens and closes the valve bodies is also provided.
此外，在該例子，作為吸入關閉時的壓縮作動室的容積Vs與各閥孔28A、28B所為的吐出開始時的壓縮作動室的容積Vd的比的設定容積比Vs/Vd，是設成閥孔28A側及28B側的兩方皆在1.5～3.0的範圍內。可是，由於閥孔28A側與28B側是與陰轉子的旋轉方向互相偏離配置，所以每個設定容積比Vs/Vd彼此不同。又，該例子中，吐出殼16的吐出側端面24的閥孔28A、28B的各自的中心也是分別幾乎位在主殼體15的端面21的內孔20B的開口緣。Further, in this example, the set volume ratio Vs/Vd which is a ratio of the volume Vs of the compression operation chamber at the time of suction closing to the volume Vd of the compression operation chamber at the start of discharge of each of the valve holes 28A and 28B is set as a valve. Both sides of the holes 28A and 28B are in the range of 1.5 to 3.0. However, since the valve hole 28A side and the 28B side are arranged to be offset from each other in the rotation direction of the female rotor, each of the set volume ratios Vs/Vd is different from each other. Moreover, in this example, the respective centers of the valve holes 28A and 28B of the discharge-side end surface 24 of the discharge case 16 are also the opening edges of the inner holes 20B which are almost at the end faces 21 of the main casing 15, respectively.
該變形例3中，也可獲得與上述實施例同樣的效果，並且閥孔由於是與轉子的旋轉方向相互偏離配置複數個，所以可使複數個閥孔合計的通路面積不會與轉子干涉，並可有效率地增大。Also in the third modification, the same effects as those of the above-described embodiment can be obtained, and since the valve holes are arranged to be offset from each other in the rotation direction of the rotor, the total passage area of the plurality of valve holes can be prevented from interfering with the rotor. It can be increased efficiently.
圖12是說明在極冷器單元裝入本發明的實施例1所示的螺旋壓縮機的冷凍循環構成圖。Fig. 12 is a view showing the configuration of a refrigeration cycle in which the screw compressor shown in the first embodiment of the present invention is incorporated in the cold cooler unit.
圖12中，130為實施例1所示的螺旋壓縮機，從該壓縮機130被吐出的冷媒氣體經由吐出配管94進入油分離器92，於此，油被分離，冷媒氣體經由配管(冷媒配管)96被送到冷凝器140。在冷凝器，冷媒氣體是以外氣被冷卻而凝縮作成液冷媒，被送到電子膨脹閥142而膨脹。在電子膨脹閥142的下游設有蒸發器141，前述膨脹的冷媒在蒸發器141從外部的冷卻水等奪取熱而蒸發，再被吸入前述壓縮機130。在前述蒸發器141被冷卻的冷卻水作為冷房用途等被使用。In Fig. 12, 130 is the screw compressor shown in the first embodiment, and the refrigerant gas discharged from the compressor 130 enters the oil separator 92 via the discharge pipe 94. Here, the oil is separated, and the refrigerant gas passes through the pipe (refrigerant pipe). 96 is sent to the condenser 140. In the condenser, the refrigerant gas is cooled and condensed as a liquid refrigerant, and is sent to the electronic expansion valve 142 to be expanded. An evaporator 141 is provided downstream of the electronic expansion valve 142, and the expanded refrigerant is taken up by the coolant 141 from external cooling water or the like to be evaporated, and then sucked into the compressor 130. The cooling water cooled by the evaporator 141 is used as a cold room or the like.
在前述壓縮機130的吸入側設有吸入壓力感測器110，並在壓縮機130的吐出側設有吐出壓力感測器111，檢知冷媒氣體的吸入壓力及吐出壓力。42是與圖6、圖7所示的電磁閥42同樣的電磁閥，該電磁閥42是依據來自控制裝置112的指令進行開閉。前述控制裝置112是依據往壓縮機130的吸入壓力與壓縮機130的吐出壓力，求出運轉中的壓力比，並將該壓力比與預先被記憶的所設定的壓力比進行比較，當運轉中的壓力比變的比前述所設定的壓力比更小時，判斷有過壓縮發生，如圖7所示，閥體驅動裝置30控制前述電磁閥42打開閥體31。A suction pressure sensor 110 is provided on the suction side of the compressor 130, and a discharge pressure sensor 111 is provided on the discharge side of the compressor 130 to detect the suction pressure and the discharge pressure of the refrigerant gas. 42 is a solenoid valve similar to the solenoid valve 42 shown in FIGS. 6 and 7, and the solenoid valve 42 is opened and closed in accordance with a command from the control device 112. The control device 112 determines the pressure ratio during operation based on the suction pressure of the compressor 130 and the discharge pressure of the compressor 130, and compares the pressure ratio with the set pressure ratio stored in advance, during operation. When the pressure ratio is smaller than the pressure ratio set as described above, it is judged that over-compression occurs, and as shown in FIG. 7, the valve body driving device 30 controls the solenoid valve 42 to open the valve body 31.
在極冷器單元，由於通常是將冷卻水的溫度控制到目標值，所以不太會有被冷卻水溫度影響的吸入壓力的變動，可是在冷凝器的冷卻凝縮壓力是當外氣變低溫時降低，所以利用吐出壓力感測器111所檢出的壓縮機的吐出側的壓力會變動。因此，在壓縮機130，過壓縮雖容易發生，可是，採用本實施例所示的螺旋壓縮機，可降低過壓縮的發生，並獲得動力損失少的極冷器單元。In the cold cooler unit, since the temperature of the cooling water is usually controlled to a target value, there is little variation in the suction pressure affected by the temperature of the cooling water, but the cooling condensing pressure in the condenser is when the external air becomes low. Since the pressure is lowered, the pressure on the discharge side of the compressor detected by the discharge pressure sensor 111 fluctuates. Therefore, in the compressor 130, although over-compression is likely to occur, the use of the screw compressor shown in this embodiment can reduce the occurrence of over-compression and obtain a cold-cooler unit with less power loss.
根據以上說明的本實施例，由於是相對於預先所設定的壓力比(吐出壓/吸入壓)，當從己測定的吸入壓力與吐出壓力所計算的壓力比高的時候，朝壓縮機的吸入側排出活塞的閥體側的汽缸內的油壓的方式關閉前述閥體，相對於預先所設定的壓力比，當從已測定的吸入壓力與吐出壓力所計算的壓力比低的時候，構成關閉前述汽缸內的油壓，打開前述閥體，所以可確實開閉閥體，並減輕過壓縮。結果，可抑制多餘的動力的消耗，並謀求性能提昇。如以往，與利用作用在閥體的壓縮作動室的壓力與吐出側的壓力和彈簧力的平衡來開閉閥的情形相比，不僅可確實開閉閥體，且藉由壓縮作動室的壓力變動可防止閥體晃動，因此，可獲得降低閥體的打擊聲或振動的螺旋壓縮機。According to the present embodiment described above, since it is a pressure ratio (discharge pressure/suction pressure) set in advance, when the pressure ratio calculated from the measured suction pressure and the discharge pressure is high, the suction toward the compressor is performed. The valve body is closed by the oil pressure in the cylinder on the valve body side of the side discharge piston, and the valve body is closed when the pressure ratio calculated from the measured suction pressure and the discharge pressure is low with respect to the previously set pressure ratio. Since the oil pressure in the cylinder opens the valve body, the valve body can be surely opened and closed, and over-compression can be alleviated. As a result, the consumption of excess power can be suppressed and performance can be improved. As compared with the case where the valve is opened and closed by the balance between the pressure acting on the compression chamber of the valve body and the pressure on the discharge side and the spring force, the valve body can be surely opened and closed, and the pressure fluctuation of the compression chamber can be controlled. The valve body is prevented from rattling, and therefore, a screw compressor that reduces the struck sound or vibration of the valve body can be obtained.
尤其，由於在活塞的閥體側的汽缸內設有朝反閥體側推壓活塞的彈簧，所以即使在壓縮作動室壓力變動產生，也不會有因前述彈簧朝制動器敲擊閥體的情況，因此，可消除閥體敲擊制動器的打擊聲及閥體的振動，又由於設在汽缸內的前述彈簧也不會有反覆激烈伸縮的情況，所以也可提昇其信賴性。In particular, since the spring that presses the piston toward the valve body side is provided in the cylinder on the valve body side of the piston, even if the pressure in the compression chamber is fluctuated, there is no possibility that the spring is struck against the valve body by the brake. Therefore, the struck sound of the valve body knocking brake and the vibration of the valve body can be eliminated, and since the spring provided in the cylinder does not have a repetitively elastic expansion and contraction, the reliability can be improved.
再者，專利文獻1所記載的習知物品，在閥體的開閉時，氣體通過閥部之際，因為流量被壓縮，所以流體摩擦變大，而無法充分減輕過壓縮。而相對於此，根據本實施例，由於藉由控制裝置，閥體被控制在全開或全閉的狀態，所以也可防止如以往，因為閥體的打開的程度的變動，壓縮從閥體部分流出的氣體，使流體摩擦變大的情形，因此可充分減輕過壓縮的情況。Further, in the conventional article described in Patent Document 1, when the valve is opened and closed, when the gas passes through the valve portion, the flow rate is compressed, so that the fluid friction is increased, and the over-compression cannot be sufficiently alleviated. On the other hand, according to the present embodiment, since the valve body is controlled to be fully open or fully closed by the control device, it is possible to prevent the compression from the valve body portion due to the change in the degree of opening of the valve body as in the related art. The outflowing gas causes the fluid to become frictionally large, so that the over-compression can be sufficiently alleviated.
1．．．壓縮機本體1. . . Compressor body
2．．．馬達2. . . motor
5．．．吸入室5. . . Inhalation chamber
6．．．吸入口6. . . suction point
9．．．吐出口9. . . Spit
10．．．旋轉軸10. . . Rotary axis
13．．．馬達殼體13. . . Motor housing
14．．．螺旋轉子(14A：陽轉子、14B：陰轉子)14. . . Spiral rotor (14A: male rotor, 14B: female rotor)
15．．．主殼體(21：端面)15. . . Main housing (21: end face)
16．．．吐出殼(24：吐出側端面)16. . . Spit shell (24: discharge side end face)
17、18．．．滾動軸承17, 18. . . Rolling bearing
19、91．．．滾珠軸承19, 91. . . Ball bearing
20．．．內孔(20A：陽轉子側內孔、20B：陰轉子側內孔)20. . . Inner hole (20A: male rotor side inner hole, 20B: female rotor side inner hole)
22．．．吸入埠(低壓空間)twenty two. . . Inhalation 埠 (low pressure space)
23、23A、23B．．．徑方向的吐出埠23, 23A, 23B. . . Spit in the radial direction埠
25、25A、25B．．．軸向的吐出埠25, 25A, 25B. . . Axial spitting
26．．．吐出室26. . . Spit room
28、28A、28B、37．．．閥孔(28a：反壓室)28, 28A, 28B, 37. . . Valve hole (28a: back pressure chamber)
29、29A、38．．．旁通溝(旁通流路)29, 29A, 38. . . Bypass groove (bypass flow path)
30．．．閥體驅動裝置30. . . Valve body drive
31．．．閥體31. . . Valve body
32．．．連通孔(氣體壓供給路)32. . . Connecting hole (gas pressure supply path)
34、120．．．油壓供給路(34：連通孔、120：毛細管)34, 120. . . Hydraulic supply path (34: communication hole, 120: capillary)
35．．．汽缸(35A、35B：汽缸室)35. . . Cylinder (35A, 35B: cylinder chamber)
36A、36B．．．壓縮作動室36A, 36B. . . Compression chamber
42．．．電磁閥42. . . The electromagnetic valve
50、54．．．密封環50, 54. . . Sealing ring
51．．．活塞51. . . piston
52．．．螺拴52. . . Screw
53．．．推桿53. . . Putt
60．．．端蓋60. . . End cap
80．．．連通路(油壓排出路)80. . . Connecting road (oil pressure discharge road)
90．．．吐出流路90. . . Spit out the flow
92．．．油分離器92. . . Oil separator
93．．．油返回配管93. . . Oil return piping
94．．．吐出配管94. . . Spit pipe
95．．．油槽95. . . Oil tank
96．．．配管(冷媒配管)96. . . Piping (refrigerant piping)
102．．．連通孔102. . . Connecting hole
110．．．吸入壓力感測器110. . . Suction pressure sensor
111．．．吐出壓力感測器111. . . Spit pressure sensor
112．．．控制裝置112. . . Control device
130．．．螺旋壓縮機130. . . Screw compressor
140．．．冷凝器140. . . Condenser
141．．．蒸發器141. . . Evaporator
142．．．電子膨脹閥142. . . Electronic expansion valve
[圖1]表示本發明的螺旋壓縮機的實施例1的縱剖視圖。Fig. 1 is a longitudinal sectional view showing a first embodiment of a screw compressor according to the present invention.
[圖2]圖1的右側視圖。FIG. 2 is a right side view of FIG. 1. FIG.
[圖3]圖1的III-III線箭頭視剖視圖。Fig. 3 is a cross-sectional view taken along line III-III of Fig. 1;
[圖4]圖1的IV-IV線箭頭視剖視圖。Fig. 4 is a cross-sectional view taken along line IV-IV of Fig. 1;
[圖5]說明本發明的實施例1的壓縮作動室、吐出埠、閥孔及旁通流路的位置關係的圖。Fig. 5 is a view for explaining a positional relationship between a compression operation chamber, a discharge port, a valve hole, and a bypass flow path in the first embodiment of the present invention.
[圖6]以圖2的VI-VI線箭頭視剖視圖表示閥體的閉狀態的圖。Fig. 6 is a cross-sectional view taken along the line VI-VI of Fig. 2, showing a closed state of the valve body.
[圖7]以圖2的VI-VI線箭頭視剖視圖表示閥裝置的開狀態的圖。Fig. 7 is a cross-sectional view taken along the line VI-VI of Fig. 2, showing a state in which the valve device is opened.
[圖8]為圖6的VIII-VIII線箭頭視剖視圖。Fig. 8 is a cross-sectional view taken along the line VIII-VIII of Fig. 6;
[圖9]以說明實施例1的變形例1的圖，表示吐出殼的吐出側端面的圖。Fig. 9 is a view for explaining a first modification of the first embodiment, showing a discharge-side end surface of the discharge casing.
[圖10]以說明實施例1的變形例2的圖表示相當於圖9的圖。FIG. 10 is a view corresponding to FIG. 9 for explaining a modification of the second embodiment.
[圖11]以說明實施例1的變形例3的圖，表示相當於圖9的圖。Fig. 11 is a view corresponding to a third modification of the first embodiment, showing a view corresponding to Fig. 9 .
[圖12]說明安裝有表示實施例1的螺旋壓縮機的極冷器單元的例子的冷凍循環構成圖。Fig. 12 is a view showing a configuration of a refrigeration cycle in which an example of a cold cooler unit showing the screw compressor of the first embodiment is mounted.
15．．．主殼體15. . . Main housing
22．．．吸入埠(低壓空間)twenty two. . . Inhalation 埠 (low pressure space)
80．．．連通路80. . . Connected road
42．．．電磁閥42. . . The electromagnetic valve
21．．．端面twenty one. . . End face
31．．．閥體31. . . Valve body
29．．．旁通溝29. . . Bypass
16．．．吐出殼16. . . Spit shell
24．．．吐出側端面twenty four. . . Discharge side face
33．．．彈簧33. . . spring
120．．．毛細管120. . . Capillary
34．．．連通孔34. . . Connecting hole
35．．．汽缸35. . . cylinder
30．．．閥體驅動裝置30. . . Valve body drive
54．．．密封環54. . . Sealing ring
51．．．活塞51. . . piston
32．．．連通孔(氣體壓供給路)32. . . Connecting hole (gas pressure supply path)
60．．．端蓋60. . . End cap
52．．．螺拴52. . . Screw
35A．．．汽缸室35A. . . Cylinder chamber
35B．．．汽缸室35B. . . Cylinder chamber
14B．．．陰轉子14B. . . Female rotor
36B．．．壓縮作動室36B. . . Compression chamber
24．．．吐出側端面twenty four. . . Discharge side face
28．．．閥孔28. . . Valve hole
28a．．．反壓室28a. . . Back pressure chamber
50．．．密封環50. . . Sealing ring
102．．．連通孔102. . . Connecting hole
101．．．桿孔101. . . Rod hole
35B．．．汽缸室35B. . . Cylinder chamber
53．．．推桿53. . . Putt
Claims (11)
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| JP2010192546A JP5389755B2 (en) | 2010-08-30 | 2010-08-30 | Screw compressor |
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| TW201217650A TW201217650A (en) | 2012-05-01 |
| TWI494508B true TWI494508B (en) | 2015-08-01 |
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| JP (1) | JP5389755B2 (en) |
| CN (1) | CN102384087B (en) |
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| JP5863609B2 (en) * | 2012-09-24 | 2016-02-16 | 日立アプライアンス株式会社 | Screw compressor and chiller unit including the same |
| GB2528214C (en) * | 2013-05-30 | 2020-01-29 | Mitsubishi Electric Corp | Screw compressor and refrigeration cycle apparatus |
| US10487833B2 (en) | 2013-12-18 | 2019-11-26 | Carrier Corporation | Method of improving compressor bearing reliability |
| TWI632298B (en) * | 2016-04-19 | 2018-08-11 | 日商日立產機系統股份有限公司 | Oil-cooled screw compressor |
| US11313370B2 (en) | 2017-12-08 | 2022-04-26 | Hitachi Industrial Equipment Systems Co., Ltd. | Liquid-injected screw compressor |
| US11162705B2 (en) | 2019-08-29 | 2021-11-02 | Hitachi-Johnson Controls Air Conditioning, Inc | Refrigeration cycle control |
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|---|---|---|---|---|
| JPS6287687A (en) * | 1985-10-11 | 1987-04-22 | Kobe Steel Ltd | Control method for screw compressor |
| JP2010077897A (en) * | 2008-09-26 | 2010-04-08 | Hitachi Appliances Inc | Screw compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| DE3434694A1 (en) | 1984-09-21 | 1986-04-10 | Bitzer Kühlmaschinenbau GmbH & Co KG, 7032 Sindelfingen | SCREW COMPRESSOR FOR GASEOUS MEDIA |
| SE461052B (en) * | 1988-04-25 | 1989-12-18 | Svenska Rotor Maskiner Ab | LIFT VALVE BY A SCREW ROTATOR |
| US5509273A (en) * | 1995-02-24 | 1996-04-23 | American Standard Inc. | Gas actuated slide valve in a screw compressor |
| JP4401408B2 (en) * | 2007-08-30 | 2010-01-20 | 日立アプライアンス株式会社 | Screw compressor capacity control device |
| JP5543746B2 (en) * | 2009-09-10 | 2014-07-09 | 株式会社前川製作所 | Overcompression prevention device for screw compressor |
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| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS6287687A (en) * | 1985-10-11 | 1987-04-22 | Kobe Steel Ltd | Control method for screw compressor |
| JP2010077897A (en) * | 2008-09-26 | 2010-04-08 | Hitachi Appliances Inc | Screw compressor |
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| JP5389755B2 (en) | 2014-01-15 |
| EP2423508A2 (en) | 2012-02-29 |
| JP2012047157A (en) | 2012-03-08 |
| CN102384087B (en) | 2014-12-10 |
| TW201217650A (en) | 2012-05-01 |
| EP2423508A3 (en) | 2016-05-18 |
| EP2423508B1 (en) | 2017-05-31 |
| ES2638569T3 (en) | 2017-10-23 |
| CN102384087A (en) | 2012-03-21 |
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