JPWO2018100911A1 - Screw compressor - Google Patents

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JPWO2018100911A1
JPWO2018100911A1 JP2018553706A JP2018553706A JPWO2018100911A1 JP WO2018100911 A1 JPWO2018100911 A1 JP WO2018100911A1 JP 2018553706 A JP2018553706 A JP 2018553706A JP 2018553706 A JP2018553706 A JP 2018553706A JP WO2018100911 A1 JPWO2018100911 A1 JP WO2018100911A1
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discharge
pressure
rotor
spaces
pressurizing
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靖明 遠藤
靖明 遠藤
幸一 松尾
幸一 松尾
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Mayekawa Manufacturing Co
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Mayekawa Manufacturing Co
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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
    • 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
    • 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
    • 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
    • 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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  • 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)

Abstract

幾つかの実施形態に係るスクリュー圧縮機は、スクリューロータと、前記スクリューロータを収容するロータケーシングと、内部容積比を変更可能な内部容積比可変弁と、を備え、前記内部容積比可変弁は、前記スクリューロータの軸方向に沿って移動可能であり被圧縮気体が吐出する吐出位置を規定する弁体と、少なくとも１個の加圧室を内蔵し、前記スクリューロータの軸方向に沿って配置され前記弁体に結合されたシリンダロッドを有するシリンダと、前記加圧室の内部で前記シリンダロッドに固定され、前記加圧室を前記スクリューロータの軸方向に沿って２個の加圧空間に仕切るピストンと、を有し、さらに、吐出ガス通路と前記２個の加圧空間の一方とに連通する第１連通路と、前記スクリューロータ及び前記ロータケーシングの間に形成される歯溝空間であって、前記吐出ポートに連通する歯溝空間より１歯溝手前の吐出直前歯溝空間と前記２個の加圧空間の他方とを連通する第２連通路と、を備える。A screw compressor according to some embodiments includes a screw rotor, a rotor casing that houses the screw rotor, and an internal volume ratio variable valve that can change an internal volume ratio, and the internal volume ratio variable valve includes: A valve body that is movable along the axial direction of the screw rotor and that defines a discharge position through which compressed gas is discharged, and at least one pressurizing chamber are built in and arranged along the axial direction of the screw rotor A cylinder having a cylinder rod coupled to the valve body, and is fixed to the cylinder rod inside the pressurizing chamber, and the pressurizing chamber is divided into two pressurizing spaces along the axial direction of the screw rotor. A piston for partitioning, a first communication passage communicating with the discharge gas passage and one of the two pressurized spaces, the screw rotor, and the rotor casing A second communicating path that is formed between the tooth space immediately before discharge and the other of the two pressure spaces, the tooth space being formed between the tooth space and the tooth space immediately preceding the tooth space. And comprising.

Description

本開示は、内部容積比可変弁を備えるスクリュー圧縮機に関する。   The present disclosure relates to a screw compressor including an internal volume ratio variable valve.

スクリュー圧縮機は、一対の雄ロータ及び雌ロータからなるスクリューロータと、スクリューロータを収容するロータケーシングとを備える。ロータケーシングには、被圧縮気体が吸入される吸入ガス通路、吸入ポートと、被圧縮気体が吐出する吐出ポート、吐出ガス通路とが形成される。
スクリューロータとロータケーシングとの間に歯溝空間が形成され、雄ロータ及び雌ロータが互いに逆方向に回転することで、吸入ポートから歯溝空間に被圧縮気体が吸入される。歯溝空間に閉じ込められた被圧縮気体は、スクリューロータの回転に伴い歯溝空間が次第に狭くなることで圧縮され、圧縮された気体が吐出ポートから吐出される。
スクリュー圧縮機は、吐出ポートに連通する直前の歯溝空間に閉じ込められた被圧縮気体の圧力が吐出ガス通路における被圧縮気体の圧力（圧縮機の吐出圧力にほぼ等しい。）と等しい場合に最も効率が良いとされる。
（圧力損失を無視し，圧縮機の吐出圧力＝吐出ガス通路における被圧縮気体の圧力＝吐出ポートから吐出される被圧縮気体の圧力として取り扱う。）The screw compressor includes a screw rotor including a pair of male rotors and female rotors, and a rotor casing that houses the screw rotors. The rotor casing is formed with an intake gas passage and an intake port through which the compressed gas is sucked, and a discharge port and a discharge gas passage through which the compressed gas is discharged.
A tooth space is formed between the screw rotor and the rotor casing, and the male rotor and the female rotor rotate in directions opposite to each other, whereby the compressed gas is sucked into the tooth space from the suction port. The compressed gas confined in the tooth space is compressed as the tooth space gradually becomes narrower as the screw rotor rotates, and the compressed gas is discharged from the discharge port.
The screw compressor is most suitable when the pressure of the compressed gas confined in the tooth space immediately before communicating with the discharge port is equal to the pressure of the compressed gas in the discharge gas passage (approximately equal to the discharge pressure of the compressor). It is said that efficiency is good.
(The pressure loss is ignored, and the discharge pressure of the compressor = the pressure of the compressed gas in the discharge gas passage = the pressure of the compressed gas discharged from the discharge port.)

歯溝空間はスクリューロータの回転に従って吐出側へ移動し、歯溝空間の容積が最大になったとき歯溝空間は吸入ポートと遮断される。この最大容積と吐出ポートに連通する直前の歯溝空間容積との比が内部容積比（最大容積／吐出直前歯溝空間容積）であり、この内部容積比を調整して最大効率を得るために内部容積比可変弁が用いられる。
内部容積比可変弁として、例えば、ロータケーシングの内部で弁体をスクリューロータの軸方向へ移動させ、被圧縮気体の吐出位置を規定するスライド弁が用いられる。スライド弁の操作方法として、弁体を手動で操作する方式や、外部の制御器からの指令により油圧回路等を使用して弁体を油圧駆動する方式が行われている。The tooth space is moved to the discharge side according to the rotation of the screw rotor, and when the volume of the tooth space reaches a maximum, the tooth space is blocked from the suction port. The ratio between the maximum volume and the tooth space space immediately before communicating with the discharge port is the internal volume ratio (maximum volume / the tooth space space immediately before discharge). In order to obtain the maximum efficiency by adjusting the internal volume ratio An internal volume ratio variable valve is used.
As the internal volume ratio variable valve, for example, a slide valve that moves the valve body in the axial direction of the screw rotor inside the rotor casing and defines the discharge position of the compressed gas is used. As a method for operating the slide valve, there are a method of manually operating the valve body and a method of hydraulically driving the valve body using a hydraulic circuit or the like according to a command from an external controller.

特許文献１には、油圧駆動のシリンダを設け、弁体をピストンロッドを介して前記シリンダの内部で摺動自在なピストンに連結し、ピストンを油圧駆動でスクリューロータの軸方向へ移動させる構成が開示されている。
特許文献２には、油圧駆動等を用いた駆動機構を不要とするため、弁体と連結したピストンを内蔵したシリンダの内部空間を３つの加圧室に区画し、これら加圧室に選択的に吐出気体又は吸入気体を導入し、吐出気体と吸入気体との差圧又は合計圧によりピストンに３段階の異なる圧力差を付与し、これによって、ピストンを３か所の位置に移動可能にした構成が開示されている。Patent Document 1 has a configuration in which a hydraulically driven cylinder is provided, a valve body is connected to a piston slidable inside the cylinder via a piston rod, and the piston is moved in the axial direction of the screw rotor by hydraulic driving. It is disclosed.
In Patent Document 2, in order to eliminate the need for a drive mechanism using hydraulic drive or the like, an internal space of a cylinder containing a piston connected to a valve body is divided into three pressurizing chambers, and these pressurizing chambers are selectively used. The discharge gas or suction gas is introduced into the piston, and the pressure difference between the discharge gas and the suction gas or the total pressure is given to the piston in three different pressure differences, so that the piston can be moved to three positions. A configuration is disclosed.

特開平１０−２２８８号公報Japanese Patent Laid-Open No. 10-2288 特開２０１４−２０６０９８号公報JP 2014-206098 A

内部容積比可変弁の弁体の位置を手動で操作する方式は、弁体の頻繁な操作は困難であり、従って、スクリュー圧縮機を常に高効率な状態を保つことは困難である。
油圧駆動により弁体を操作する方式は、弁体を移動させるための油圧機器や電磁弁などの補器類、及び各種センサを含む制御用機器を必要とし高コストとなる。
特許文献２に開示された手段では、弁体を駆動する油圧機器類が不要になる利点があるが、スライド弁の弁体の位置が３か所に限られ、連続的な位置制御ができないという問題がある。また、吐出ポートに連通する直前の歯溝空間に閉じ込められた被圧縮気体の圧力が吐出ガス通路における被圧縮気体の圧力と等しくなるように弁体の位置を調整することはできない。In the method of manually operating the position of the valve body of the internal volume ratio variable valve, frequent operation of the valve body is difficult, and therefore, it is difficult to always keep the screw compressor in a highly efficient state.
The method of operating the valve body by hydraulic drive requires a hydraulic device for moving the valve body, auxiliary equipment such as an electromagnetic valve, and a control device including various sensors, and is expensive.
The means disclosed in Patent Document 2 has an advantage that hydraulic devices for driving the valve body are not required, but the position of the valve body of the slide valve is limited to three locations, and continuous position control cannot be performed. There's a problem. Further, the position of the valve body cannot be adjusted so that the pressure of the compressed gas confined in the tooth space immediately before communicating with the discharge port becomes equal to the pressure of the compressed gas in the discharge gas passage.

幾つかの実施形態は、高コストとなる駆動用機器及び制御用機器を必要とせずに、吐出直前の歯溝空間における被圧縮気体の圧力を圧縮機の吐出圧力と等しくすることで、スクリュー圧縮機の効率を向上させることを目的とする。   In some embodiments, screw compression is achieved by making the pressure of the compressed gas in the tooth space immediately before discharge equal to the discharge pressure of the compressor without requiring expensive driving and control devices. The purpose is to improve the efficiency of the machine.

（１）幾つかの実施形態に係るスクリュー圧縮機は、
一対の雄ロータ及び雌ロータを含むスクリューロータと、
前記スクリューロータを収容すると共に、被圧縮気体が吸入される吸入ガス通路、吸入ポート及び被圧縮気体が吐出する吐出ポート、吐出ガス通路が形成されるロータケーシングと、
内部容積比を変更可能な内部容積比可変弁と、
を備えるスクリュー圧縮機であって、
前記内部容積比可変弁は、
前記ロータケーシングの内部に設けられ、前記スクリューロータの軸方向に沿って移動可能であり、前記被圧縮気体が前記スクリューロータと前記ロータケーシングとの間に形成される歯溝空間から前記吐出ポートに吐出する吐出位置を規定する弁体と、
少なくとも１個の加圧室を内蔵し、前記弁体に結合され前記スクリューロータの軸方向に沿って配置されたシリンダロッド、及び前記加圧室の内部で前記シリンダロッドに固定され、前記加圧室を前記スクリューロータの軸方向に沿って２個の加圧空間に仕切るピストンを有するシリンダと、
を備え、
さらに、前記吐出ガス通路と前記２個の加圧空間の一方とに連通する第１連通路と、
前記吐出ポートに連通する歯溝空間より１歯溝手前の吐出直前歯溝空間と前記２個の加圧空間の他方とを連通する第２連通路と、
を備える。(1) A screw compressor according to some embodiments,
A screw rotor including a pair of male and female rotors;
A rotor casing in which the screw rotor is accommodated, a suction gas passage through which compressed gas is sucked, a suction port and a discharge port through which the compressed gas is discharged, and a discharge gas passage;
An internal volume ratio variable valve capable of changing the internal volume ratio;
A screw compressor comprising:
The internal volume ratio variable valve is:
It is provided inside the rotor casing and is movable along the axial direction of the screw rotor, and the compressed gas is transferred from a tooth space formed between the screw rotor and the rotor casing to the discharge port. A valve body that defines a discharge position to be discharged;
At least one pressurizing chamber is built in, and is connected to the valve body and arranged along the axial direction of the screw rotor, and is fixed to the cylinder rod inside the pressurizing chamber, and the pressurizing chamber A cylinder having a piston partitioning the chamber into two pressurizing spaces along the axial direction of the screw rotor;
With
A first communication passage communicating with the discharge gas passage and one of the two pressurized spaces;
A second communication path that communicates the tooth space immediately before the tooth gap with the other one of the two pressure spaces with respect to the tooth space that communicates with the discharge port;
Is provided.

上記内部容積比可変弁を構成する上記ピストンには、上記２つの加圧空間に供給される気体の圧力が付加されるため、スクリューロータの軸方向（以下「ロータ軸方向」とも言う。）に沿う互いに逆方向の力が加わる。
上記２つの加圧空間の一方には上記第１連通路を介して吐出ガス通路の気体が導入されるため、ピストンに吐出気体の圧力が加わる。上記２つの加圧空間の他方には、上記第２連通路を介して上記吐出直前歯溝空間から被圧縮気体が導入され、この被圧縮気体の圧力がピストンに加わる。
弁体はピストンに両側から加わる上記圧力の差によってロータ軸方向に移動する。ピストンに両側から加わる圧力が等しくなったとき、内部容積比可変弁の弁体のスクリューロータ軸方向の動きは停止する。Since the pressure of the gas supplied to the two pressurized spaces is applied to the piston constituting the internal volume ratio variable valve, the axial direction of the screw rotor (hereinafter also referred to as “rotor axial direction”). Forces in opposite directions are applied.
Since the gas in the discharge gas passage is introduced into one of the two pressurized spaces through the first communication passage, the pressure of the discharge gas is applied to the piston. A compressed gas is introduced into the other of the two pressurized spaces from the tooth space immediately before discharge through the second communication path, and the pressure of the compressed gas is applied to the piston.
The valve body moves in the rotor axial direction due to the pressure difference applied to the piston from both sides. When the pressure applied to the piston from both sides becomes equal, the movement of the internal volume ratio variable valve in the axial direction of the screw rotor stops.

このように、弁体は、吐出ガス通路の吐出圧力と吐出直前歯溝空間の圧力が等しくなる位置に自動的に移動するため、吐出ガス通路の被圧縮気体の圧力と吐出直前歯溝空間の被圧縮気体の圧力とは常に等しくなる。このように、弁体を自動的かつ連続的に移動させて常に最適位置に設定できるため、常に、スクリュー圧縮機を最も効率良く稼働させることができる。他方、弁体は、ピストンの両側に加わる圧力の差によって作動するため、弁体を駆動し制御するための駆動用機器及び制御用機器を必要としない。   In this way, the valve body automatically moves to a position where the discharge pressure in the discharge gas passage and the pressure in the tooth space immediately before discharge become equal, so the pressure of the compressed gas in the discharge gas passage and the space in the tooth space just before discharge The pressure of the compressed gas is always equal. Thus, the valve body can be automatically and continuously moved and always set to the optimum position, so that the screw compressor can always be operated most efficiently. On the other hand, since the valve body is operated by a difference in pressure applied to both sides of the piston, a driving device and a control device for driving and controlling the valve body are not required.

（２）一実施形態では、前記（１）の構成において、
前記２個の加圧空間の一方は前記ピストンに対して前記吸入ポート側に位置し、
前記２個の加圧空間の他方は前記ピストンに対して前記吐出ポート側に位置する。
上記（２）の構成によれば、上記２個の加圧空間の一方に圧縮機の吐出圧が伝わり、上記２個の加圧空間の他方に吐出直前歯溝空間の圧力が伝わる。
これによって、例えば、圧縮機の吐出圧が高ければ、内部容積比可変弁の弁体は吐出ポート側へ押し出され、吐出直前歯溝空間の圧力が高ければ、内部容積比可変弁の弁体は吸入ポート側へ押し出される。こうして、被圧縮気体の吐出直前歯溝空間の圧力が、吐出ガス通路の圧力と同じになるように、自動的に調整される。(2) In one embodiment, in the configuration of (1),
One of the two pressure spaces is located on the suction port side with respect to the piston,
The other of the two pressure spaces is located on the discharge port side with respect to the piston.
According to the configuration of (2), the discharge pressure of the compressor is transmitted to one of the two pressure spaces, and the pressure in the tooth space immediately before discharge is transmitted to the other of the two pressure spaces.
Thus, for example, if the discharge pressure of the compressor is high, the valve body of the internal volume ratio variable valve is pushed to the discharge port side, and if the pressure in the tooth space immediately before discharge is high, the valve body of the internal volume ratio variable valve is It is pushed out to the suction port side. Thus, the pressure in the tooth space immediately before the discharge of the compressed gas is automatically adjusted so as to be the same as the pressure in the discharge gas passage.

（３）一実施形態では、前記（１）又は（２）の構成において、
前記弁体は、前記吸入ガス通路に連通した、吸入圧力のガスで満たされた空間（以下、「吸入ガス空間」とも言う。）に面した第１端面及び前記吐出ガス通路に面した第２端面を有し、
前記シリンダは、前記スクリューロータの軸方向に沿って配置された第１加圧室及び第２加圧室を内蔵し、
前記第１加圧室において、前記ピストンによって仕切られた前記２個の加圧空間の一方が前記第１連通路に連通すると共に、前記２個の加圧空間の他方が前記第２連通路に連通し、
前記第２加圧室において、前記ピストンによって仕切られた前記２個の加圧空間のうち、前記ピストンを前記吐出ポート側から前記吸入ポート側へ加圧する正方向加圧空間と前記吸入ガス通路とを連通する第３連通路と、
前記第２加圧室に形成される前記２個の加圧空間のうち、前記ピストンを前記吸入ポート側から前記吐出ポート側へ加圧する逆方向加圧空間と前記吐出ガス通路とを連通する第４連通路と、
を備え、
前記第１端面が前記吸入ガス空間の前記被圧縮気体から加圧される受圧面と前記正方向加圧空間における前記ピストンの受圧面の面積が等しく、かつ前記第２端面が前記吐出ガス通路の前記被圧縮気体から加圧される受圧面と前記逆方向加圧空間における前記ピストンの受圧面の面積が等しい。(3) In one embodiment, in the configuration of (1) or (2),
The valve body communicates with the suction gas passage and has a first end face facing a space filled with gas of suction pressure (hereinafter also referred to as “suction gas space”) and a second end face facing the discharge gas passage. Having an end face,
The cylinder includes a first pressurizing chamber and a second pressurizing chamber disposed along the axial direction of the screw rotor,
In the first pressurizing chamber, one of the two pressurizing spaces partitioned by the piston communicates with the first communicating path, and the other of the two pressurizing spaces communicates with the second communicating path. Communication,
In the second pressurizing chamber, of the two pressurizing spaces partitioned by the piston, a positive pressurizing space for pressurizing the piston from the discharge port side to the suction port side, and the suction gas passage, A third communication passage that communicates with each other;
Of the two pressurization spaces formed in the second pressurization chamber, a reverse pressurization space for pressurizing the piston from the suction port side to the discharge port side and a discharge gas passage communicate with each other. 4 passages,
With
The area of the pressure receiving surface where the first end surface is pressurized from the compressed gas in the suction gas space and the pressure receiving surface of the piston in the positive direction pressure space are equal, and the second end surface is the discharge gas passage. The area of the pressure receiving surface of the piston in the reverse pressure space is equal to the pressure receiving surface pressurized from the compressed gas.

上記実施形態は、内部容積比可変弁の弁体が吸入ガス空間に面した第１端面及び吐出ガス通路に面した第２端面を有し、第１端面には吸入ポートからスクリューロータに吸入される被圧縮気体の圧力が加わり、第２端面には吐出ポートから吐出ガス通路に吐出される被圧縮気体の圧力が加わる場合の実施形態である。
この実施形態では、上記第２加圧室において、上記正方向加圧空間に吸入ガス通路の被圧縮気体を導入することで、第１端面が受ける吸入ガス空間の被圧縮気体から受ける圧力と同等でかつ逆向きの圧力をピストンに加える。また、第２加圧室の上記逆方向加圧空間に吐出ガス通路の被圧縮気体を導入することで、第２端面が吐出ガス通路の被圧縮気体から受ける圧力と同等でかつ逆向きの圧力をピストンに加える。
これによって、内部容積比可変弁の弁体が吐出ガス通路及び吸入ガス空間から受ける圧力を相殺できるため、弁体は第１加圧室のピストンに加わる圧力のみによって作動される。
なお、第１加圧室と第２加圧室とは、ロータ軸方向でどちらを吐出ポート側に近い位置に配置してもよい。In the above embodiment, the valve body of the internal volume ratio variable valve has a first end face facing the suction gas space and a second end face facing the discharge gas passage, and the first end face is sucked into the screw rotor from the suction port. In this embodiment, the pressure of the gas to be compressed is applied, and the pressure of the gas to be compressed discharged from the discharge port to the discharge gas passage is applied to the second end surface.
In this embodiment, in the second pressurizing chamber, the pressure received from the compressed gas in the suction gas space received by the first end surface is introduced by introducing the compressed gas in the suction gas passage into the positive pressure space. And reverse pressure is applied to the piston. Further, by introducing the compressed gas in the discharge gas passage into the reverse pressure space of the second pressurizing chamber, the second end face is equivalent to the pressure received from the compressed gas in the discharge gas passage and has a reverse pressure. To the piston.
Thus, the valve body of the internal volume ratio variable valve can cancel the pressure received from the discharge gas passage and the suction gas space, so that the valve body is operated only by the pressure applied to the piston of the first pressurizing chamber.
Note that either the first pressurizing chamber or the second pressurizing chamber may be disposed at a position close to the discharge port side in the rotor axial direction.

（４）一実施形態では、前記（１）〜（３）の何れかの構成において、
前記第２連通路は、
前記弁体及び前記シリンダロッドに形成された中空部と、
前記弁体に形成され前記吐出直前歯溝空間と前記中空部とを連通する第１連通孔と、
前記シリンダロッドに形成され前記中空部と前記２個の加圧空間の他方とを連通する第２連通孔と、
で構成される。
上記（４）の構成によれば、第２連通路を弁体及びシリンダロッドの内部に形成することで、弁体及びシリンダロッドの外部に第２連通路を形成するためのスペースが不要になり、スクリュー圧縮機をコンパクト化できる。(4) In one embodiment, in any one of the configurations (1) to (3),
The second communication path is
A hollow portion formed in the valve body and the cylinder rod;
A first communication hole formed in the valve body and communicating with the tooth space immediately before discharge and the hollow portion;
A second communication hole formed in the cylinder rod and communicating the hollow portion and the other of the two pressure spaces;
Consists of.
According to the configuration of (4) above, the second communication path is formed inside the valve body and the cylinder rod, so that a space for forming the second communication path outside the valve body and the cylinder rod becomes unnecessary. The screw compressor can be made compact.

（５）一実施形態では、前記（１）〜（３）の何れかの構成において、
前記第２連通路は、前記スクリューロータの吐出側端に対面する前記ロータケーシングに形成された通路を有し、前記通路は前記ロータケーシングの壁面から前記吐出直前歯溝空間に開口する開口を有する。
上記（５）の構成によれば、吐出直前歯溝空間が吐出ポートに最も接近した位置で、上記開口及び上記通路を介して吐出直前歯溝空間と第２連通路とを連通できる。これによって、吐出直前歯溝空間の被圧縮気体の圧力と吐出ポートから吐出する被圧縮気体の圧力に一致させるための精度を向上できる。(5) In one embodiment, in any one of the configurations (1) to (3),
The second communication passage has a passage formed in the rotor casing facing the discharge side end of the screw rotor, and the passage has an opening that opens from the wall surface of the rotor casing to the tooth space immediately before discharge. .
According to the configuration of (5), the immediately preceding tooth space and the second communicating passage can be communicated with each other through the opening and the passage at a position where the immediately preceding tooth space is closest to the discharge port. Thereby, the precision for making it correspond with the pressure of the to-be-compressed gas of the tooth space immediately before discharge and the to-be-compressed gas discharged from a discharge port can be improved.

（６）一実施形態では、前記（１）〜（５）の何れかの構成において、
前記シリンダは、前記スクリューロータの軸方向に沿って配置された第１加圧室及び第２加圧室を内蔵し、
前記第１加圧室は前記第２加圧室より前記スクリューロータの吐出ポート側に位置し、
前記第１加圧室に形成される前記２個の加圧空間のうち、前記２個の加圧空間の他方は前記２個の加圧空間の一方より前記スクリューロータの吐出ポート側に位置する。
上記（６）の構成によれば、第１加圧室及び第２加圧室が形成する加圧空間のうち、第２連通路が連通する上記２個の加圧空間の他方を吐出ポート側へ最も近接させて配置できる。これによって、弁体及びロッドに形成される中空部の容積を縮小でき、第２連通路の形成が容易になる。(6) In one embodiment, in any one of the configurations (1) to (5),
The cylinder includes a first pressurizing chamber and a second pressurizing chamber disposed along the axial direction of the screw rotor,
The first pressurizing chamber is located on the discharge port side of the screw rotor from the second pressurizing chamber,
Of the two pressurizing spaces formed in the first pressurizing chamber, the other of the two pressurizing spaces is located closer to the discharge port side of the screw rotor than one of the two pressurizing spaces. .
According to the configuration of (6) above, the other of the two pressurizing spaces communicating with the second communication path among the pressurizing spaces formed by the first pressurizing chamber and the second pressurizing chamber is on the discharge port side. Can be placed closest to. Thereby, the volume of the hollow part formed in the valve body and the rod can be reduced, and the formation of the second communication path is facilitated.

幾つかの実施形態によれば、スクリュー圧縮機の稼働中、吐出直前の歯溝空間における被圧縮気体の圧力を吐出ポートから吐出される被圧縮気体の圧力と常に等しくすることができ、これによって、常にスクリュー圧縮機を高効率で運転できる。また、内部容積比可変弁の弁体を操作するために、駆動用機器及び制御用機器を必要としないため低コスト化できる。   According to some embodiments, during operation of the screw compressor, the pressure of the compressed gas in the tooth space immediately before discharge can always be made equal to the pressure of the compressed gas discharged from the discharge port, thereby The screw compressor can always be operated with high efficiency. In addition, since the drive device and the control device are not required to operate the valve body of the internal volume ratio variable valve, the cost can be reduced.

一実施形態に係るスクリュー圧縮機の縦断正面図である。It is a vertical front view of the screw compressor concerning one embodiment. 一実施形態に係るスクリュー圧縮機の縦断正面図である。It is a vertical front view of the screw compressor concerning one embodiment. 一実施形態に係る内部容積比可変弁を一部断面で示す上面図である。It is a top view which shows the internal volume ratio variable valve which concerns on one Embodiment in a partial cross section. 一実施形態に係る内部容積比可変弁の縦断正面図である。It is a vertical front view of the internal volume ratio variable valve which concerns on one Embodiment. 一実施形態に係る弁体の端面を示し、図４中のＡ方向から視た正面図である。It is the front view which showed the end surface of the valve body which concerns on one Embodiment, and was seen from the A direction in FIG. 一実施形態に係る内部容積比可変弁及びロータケーシングの斜視図である。It is a perspective view of an internal volume ratio variable valve and a rotor casing according to an embodiment. 吐出直前歯溝圧力が最適な場合を示すグラフである。It is a graph which shows the case where the tooth gap pressure just before discharge is optimal. 吐出直前歯溝圧力が過圧縮である場合を示すグラフである。It is a graph which shows the case where the tooth gap pressure just before discharge is overcompression. 吐出直前歯溝圧力が圧縮不足である場合を示すグラフである。It is a graph which shows the case where the tooth gap pressure just before discharge is under compression.

以下、添付図面を参照して本発明の幾つかの実施形態について説明する。ただし、実施形態として記載され又は図面に示されている構成部品の寸法、材質、形状、その相対的配置等は、本発明の範囲をこれに限定する趣旨ではなく、単なる説明例にすぎない。
例えば、「ある方向に」、「ある方向に沿って」、「平行」、「直交」、「中心」、「同心」或いは「同軸」等の相対的或いは絶対的な配置を表す表現は、厳密にそのような配置を表すのみならず、公差、若しくは、同じ機能が得られる程度の角度や距離をもって相対的に変位している状態も表すものとする。
例えば、「同一」、「等しい」及び「均質」等の物事が等しい状態であることを表す表現は、厳密に等しい状態を表すのみならず、公差、若しくは、同じ機能が得られる程度の差が存在している状態も表すものとする。
例えば、四角形状や円筒形状等の形状を表す表現は、幾何学的に厳密な意味での四角形状や円筒形状等の形状を表すのみならず、同じ効果が得られる範囲で、凹凸部や面取り部等を含む形状も表すものとする。
一方、一つの構成要素を「備える」、「具える」、「具備する」、「含む」、又は「有する」という表現は、他の構成要素の存在を除外する排他的な表現ではない。Hereinafter, some embodiments of the present invention will be described with reference to the accompanying drawings. However, the dimensions, materials, shapes, relative arrangements, and the like of the components described in the embodiments or shown in the drawings are not intended to limit the scope of the present invention, but are merely illustrative examples.
For example, expressions expressing relative or absolute arrangements such as “in a certain direction”, “along a certain direction”, “parallel”, “orthogonal”, “center”, “concentric” or “coaxial” are strictly In addition to such an arrangement, it is also possible to represent a state of relative displacement with an angle or a distance such that tolerance or the same function can be obtained.
For example, an expression indicating that things such as “identical”, “equal”, and “homogeneous” are in an equal state not only represents an exactly equal state, but also has a tolerance or a difference that can provide the same function. It also represents the existing state.
For example, expressions representing shapes such as quadrangular shapes and cylindrical shapes represent not only geometrically strict shapes such as quadrangular shapes and cylindrical shapes, but also irregularities and chamfers as long as the same effects can be obtained. A shape including a part or the like is also expressed.
On the other hand, the expressions “comprising”, “comprising”, “comprising”, “including”, or “having” one constituent element are not exclusive expressions for excluding the existence of other constituent elements.

幾つかの実施形態に係るスクリュー圧縮機１０（１０Ａ、１０Ｂ）は、図１及び図２に示すように、ロータケーシング１２の内部に一対の雄ロータ及び雌ロータからなるスクリューロータ１４が収容される。ロータケーシング１２には、被圧縮気体Ｇが吸入される吸入ガス通路１５、吸入ポート１６、及びスクリューロータ１４で圧縮された被圧縮気体Ｇが吐出される吐出ポート１８、吐出ガス通路１９が形成される。また、内部容積比を変更可能な内部容積比可変弁２０が設けられる。
スクリューロータ１４とロータケーシング１２との間に、ロータ軸方向に沿って複数の歯溝空間Ｓｔ１、Ｓｔ２、・・・が形成される。As shown in FIGS. 1 and 2, the screw compressor 10 (10 </ b> A, 10 </ b> B) according to some embodiments accommodates a screw rotor 14 including a pair of male and female rotors in a rotor casing 12. . The rotor casing 12 is formed with a suction gas passage 15 through which the compressed gas G is sucked, a suction port 16, a discharge port 18 through which the compressed gas G compressed by the screw rotor 14 is discharged, and a discharge gas passage 19. The Further, an internal volume ratio variable valve 20 capable of changing the internal volume ratio is provided.
A plurality of tooth space St 1 , St 2 ,... Is formed between the screw rotor 14 and the rotor casing 12 along the rotor axial direction.

内部容積比可変弁２０は、弁体２２と、シリンダロッド２６が弁体２２に結合されたシリンダ２４とを有する。弁体２２は、ロータケーシング１２の内部に設けられ、ロータ軸方向に沿って移動可能であり、吐出ポート１８において被圧縮気体Ｇが吐出する吐出位置を規定する。シリンダ２４は、例えば、ロータケーシング１２の外部に突出して配置され、少なくとも１個の加圧室２８を内蔵する。シリンダロッド２６はロータ軸方向に沿って配置され、一端が弁体２２に連結し、他端側は加圧室２８に導設される。ピストン３０は加圧室２８に配置されシリンダロッド２６に固定される。加圧室２８はピストン３０によってロータ軸方向に沿って２個の加圧空間ｓ１及びｓ２に仕切られる。   The internal volume ratio variable valve 20 includes a valve body 22 and a cylinder 24 in which a cylinder rod 26 is coupled to the valve body 22. The valve body 22 is provided inside the rotor casing 12, is movable along the rotor axial direction, and defines a discharge position at which the compressed gas G is discharged at the discharge port 18. The cylinder 24 is disposed, for example, so as to protrude outside the rotor casing 12 and incorporates at least one pressurizing chamber 28. The cylinder rod 26 is disposed along the rotor axial direction, one end is connected to the valve body 22, and the other end is led to the pressurizing chamber 28. The piston 30 is disposed in the pressurizing chamber 28 and is fixed to the cylinder rod 26. The pressurizing chamber 28 is partitioned by the piston 30 into two pressurizing spaces s1 and s2 along the rotor axial direction.

さらに、２個の加圧空間ｓ１、ｓ２のうち加圧空間ｓ２と吐出ガス通路１９とに連通する第１連通路３２が設けられる。スクリューロータ１４の軸方向吐出側端に形成され吐出ポート１８に連通する歯溝空間Ｓｔ１より１歯溝手前の歯溝空間Ｓｔ２と、２個の加圧空間ｓ１、ｓ２のうち加圧空間ｓ１とを連通する第２連通路３４が設けられる。Further, a first communication passage 32 that communicates with the pressurization space s2 and the discharge gas passage 19 among the two pressurization spaces s1 and s2 is provided. A tooth gap space St 2 that is formed at the axial discharge side end of the screw rotor 14 and communicates with the discharge port 18 and one tooth space before the tooth gap space St 1 , and a pressure space of the two pressure spaces s 1 and s 2 A second communication path 34 that communicates with s1 is provided.

上記構成において、スクリューロータ１４の回転によって吸入ポート１６から歯溝空間に吸入され、歯溝空間に閉じ込められた被圧縮気体Ｇは、吐出ポート１８に向かって歯溝空間が次第に狭くなることで圧縮され、圧縮された気体が吐出ポート１８から設定された吐出圧力Ｐｄとなって吐出される。
加圧空間ｓ２には、第１連通路３２を介して吐出ポート１８から吐出され吐出圧力Ｐｄを有する被圧縮気体Ｇが導入される。加圧空間ｓ１には第２連通路３４を介して中間圧力Ｐｍを有する吐出直前歯溝空間Ｓｔ２の被圧縮気体Ｇが導入される。
図３及び図４に示すように、加圧室２８を２つの加圧空間ｓ１及びｓ２に仕切るピストン３０には、加圧空間ｓ１及びｓ２の各々に供給される被圧縮気体によって、ロータ軸方向に沿う互いに逆方向の力ｆ１及びｆ２が加わる。In the above configuration, the compressed gas G sucked into the tooth space from the suction port 16 by the rotation of the screw rotor 14 and confined in the tooth space is compressed as the tooth space is gradually narrowed toward the discharge port 18. Then, the compressed gas is discharged from the discharge port 18 at the discharge pressure Pd set.
A compressed gas G having a discharge pressure Pd discharged from the discharge port 18 through the first communication path 32 is introduced into the pressurized space s2. A gas G to be compressed in the tooth space St 2 immediately before discharge having an intermediate pressure Pm is introduced into the pressurizing space s1 through the second communication passage 34.
As shown in FIGS. 3 and 4, the piston 30 that divides the pressurizing chamber 28 into two pressurizing spaces s1 and s2 has a rotor axial direction due to the compressed gas supplied to each of the pressurizing spaces s1 and s2. Forces f 1 and f 2 in the opposite directions along the line are applied.

図７に示すように、吐出直前歯溝空間Ｓｔ２の圧力Ｐｍが歯溝空間Ｓｔ１の吐出圧力Ｐｄと等しいときに、スクリュー圧縮機１０の運転効率が最も向上する。
図８に示す運転例は、吐出直前歯溝空間Ｓｔ２の圧力Ｐｍが吐出圧力Ｐｄより高くなる場合であり、動力ロスＬｐが生じて運転効率は低下する。
図９に示す運転例は、吐出直前歯溝空間Ｓｔ２の被圧縮気体Ｇの圧力が設定された吐出圧力より低い場合であり、この場合、吐出ポート１８から被圧縮気体Ｇが吐出中の歯溝空間に逆流して歯溝空間の圧力が吐出圧力Ｐｄまで上昇し、逆流した被圧縮気体Ｇを再び吐出ポート１８から吐出ガス通路１９へ押し出す余分な仕事が発生するため、圧縮効率が低下する。As shown in FIG. 7, the pressure Pm of the discharge just before the tooth groove space St 2 is at equal to the discharge pressure Pd of the tooth spaces St 1, operation efficiency of the screw compressor 10 is most improved.
Operation example shown in FIG. 8 shows the case where the pressure Pm of the discharge just before the tooth groove space St 2 is higher than the discharge pressure Pd, the operating efficiency power loss Lp is generated is reduced.
Operation example shown in FIG. 9 shows the case the pressure of the compressed gas G of the discharge just before the tooth groove space St 2 is lower than the set discharge pressure, teeth in this case, in the compressed gas G is discharged from the discharge port 18 Backflow into the groove space increases the pressure in the tooth space to the discharge pressure Pd, and extra work for pushing the backflowed compressed gas G from the discharge port 18 back to the discharge gas passage 19 occurs, resulting in a reduction in compression efficiency. .

図１及び図２において、内部容積比可変弁２０の弁体２２は、ピストン３０に両側から加わる圧力（力）ｆ１及びｆ２の差圧によってロータ軸方向に移動する。圧力（力）ｆ１及びｆ２が等しくなったとき、即ち、吐出ポート１８から吐出される被圧縮気体Ｇの吐出圧力Ｐｄと、吐出直前歯溝空間Ｓｔ２の被圧縮気体Ｇの圧力（中間圧力Ｐｍ）とが等しくなったとき、弁体２２のロータ軸方向の動きは停止する。
このように、弁体２２は吐出圧力Ｐｄと中間圧力Ｐｍとが等しくなるロータ軸方向位置に自動的に停止するため、吐出圧力Ｐｄと中間圧力Ｐｍとは常に等しくなる。このように、吐出ポート１８の吐出位置を自動的かつ連続的に最適位置に調整できるため、スクリュー圧縮機１０を常に最も効率良く稼働させることができる。
他方、弁体２２は、ピストン３０の両側に加わる圧力の差によって作動するため、内部容積比可変弁２０を駆動しかつ制御する駆動用機器及び制御用機器を必要とせず低コスト化できる。1 and 2, the valve body 22 of the internal volume ratio variable valve 20 moves in the rotor axial direction by the differential pressure between the pressures (forces) f 1 and f 2 applied to the piston 30 from both sides. When the pressure (force) f1 and f2 are equal, i.e., the discharge pressure Pd of the compressed gas G discharged from the discharge port 18, the pressure of the compressed gas G of the discharge just before the tooth groove space St 2 (intermediate pressure Pm ) Becomes equal, the movement of the valve element 22 in the rotor axial direction stops.
Thus, since the valve body 22 automatically stops at the rotor axial direction position where the discharge pressure Pd and the intermediate pressure Pm are equal, the discharge pressure Pd and the intermediate pressure Pm are always equal. Thus, since the discharge position of the discharge port 18 can be adjusted automatically and continuously to the optimal position, the screw compressor 10 can always be operated most efficiently.
On the other hand, since the valve body 22 is operated by the difference in pressure applied to both sides of the piston 30, it is possible to reduce the cost without requiring a drive device and a control device for driving and controlling the internal volume ratio variable valve 20.

一実施形態では、図１及び図２に示すように、吐出ガス通路１９に第１連通路３２を介して連通する加圧空間ｓ２は、ピストン３０に対して吸入ポート側に位置する。吐出直前歯溝空間Ｓｔ２に連通する加圧空間ｓ１はピストン３０に対して吐出ポート側に位置する。そのため、加圧空間ｓ２に吐出圧が伝わり、加圧空間ｓ１に吐出直前歯溝空間Ｓｔ２の圧力が伝わる。
これによって、例えば、被圧縮気体Ｇの吐出圧が高ければ、内部容積比可変弁２０の弁体２２は吐出ポート側へ押し出され、吐出直前歯溝空間Ｓｔ２の圧力が高ければ、内部容積比可変弁２０の弁体２２は吸入ポート側へ押し出される。こうして、被圧縮気体Ｇの吐出直前歯溝空間Ｓｔ２の圧力が圧縮機の吐出圧力と等しくなるように自動的に調整される。In one embodiment, as shown in FIGS. 1 and 2, the pressurized space s <b> 2 that communicates with the discharge gas passage 19 via the first communication passage 32 is located on the suction port side with respect to the piston 30. A pressurizing space s1 communicating with the tooth space immediately before discharge St2 is located on the discharge port side with respect to the piston 30. Therefore, the pressurized space discharge pressure is transmitted to s2, the pressure immediately before discharging the pressurized space s1 tooth space St 2 is transmitted.
Accordingly, for example, if the discharge pressure of the compressed gas G is high, the valve body 22 of the internal volume ratio variable valve 20 is pushed out to the discharge port side, and if the pressure in the tooth space St2 immediately before discharge is high, the internal volume ratio is variable. The valve body 22 of the valve 20 is pushed out to the suction port side. In this way, the pressure in the tooth gap space St2 immediately before the discharge of the compressed gas G is automatically adjusted to be equal to the discharge pressure of the compressor.

一実施形態では、図３〜図５に示すように、吐出ガス通路１９に面した弁体２２の第２端面３８に吐出ポート１８の一部（吐出位置を規定するための切欠き４０）が形成される。
また、図３及び図４に示すように、ロータケーシング１２は吸入側端面４２及び吐出側端面４４を有する。
歯溝空間Ｓｔ１が吐出ポート１８に連通したとき、歯溝空間Ｓｔ１に閉じ込められていた被圧縮気体Ｇは吐出ポート１８に吐出する。
図４の一点鎖線４５は、スクリューロータ１４を構成する雄ロータ又は雌ロータの回転中心軸線を示す。In one embodiment, as shown in FIGS. 3 to 5, a part of the discharge port 18 (notch 40 for defining the discharge position) is formed on the second end surface 38 of the valve body 22 facing the discharge gas passage 19. It is formed.
As shown in FIGS. 3 and 4, the rotor casing 12 has a suction side end face 42 and a discharge side end face 44.
When tooth spaces St 1 is communicated with the discharge port 18, the compressed gas G which has been confined in tooth spaces St 1 is discharged into the discharge port 18.
An alternate long and short dash line 45 in FIG. 4 indicates the rotation center axis of the male rotor or the female rotor constituting the screw rotor 14.

幾つかの実施形態では、図１及び図２に示すように、弁体２２は、吸入ガス通路１５に連通した吸入ガス空間２１に面した第１端面３６及び吐出ガス通路１９に面した第２端面３８を有する。シリンダ２４は、ロータ軸方向に沿って配置された第１加圧室２８及び第２加圧室４６を有する。
第１加圧室２８及び第２加圧室４６にはシリンダロッド２６が導設される。第１加圧室２８にピストン３０が設けられ、第２加圧室４６にピストン４８が設けられる。シリンダロッド２６にピストン３０及び４８が固定される。第１加圧室２８では、ピストン３０によって加圧空間ｓ１及びｓ２がロータ軸方向に仕切られ、第２加圧室４６では、加圧空間ｓ３及びｓ４がロータ軸方向に仕切られる。In some embodiments, as shown in FIGS. 1 and 2, the valve body 22 has a first end face 36 facing the intake gas space 21 communicating with the intake gas passage 15 and a second end face facing the discharge gas passage 19. An end surface 38 is provided. The cylinder 24 has a first pressurizing chamber 28 and a second pressurizing chamber 46 arranged along the rotor axial direction.
A cylinder rod 26 is led to the first pressurizing chamber 28 and the second pressurizing chamber 46. A piston 30 is provided in the first pressurizing chamber 28, and a piston 48 is provided in the second pressurizing chamber 46. Pistons 30 and 48 are fixed to the cylinder rod 26. In the first pressurizing chamber 28, the pressurizing spaces s1 and s2 are partitioned in the rotor axial direction by the piston 30, and in the second pressurizing chamber 46, the pressurizing spaces s3 and s4 are partitioned in the rotor axial direction.

図３及び図４に示すように、ピストン４８は、正方向加圧空間ｓ３に供給される気体によってスクリューロータ１４の吐出側から吸入側へ向かう力ｆ３を受け、逆方向加圧空間ｓ４に供給される気体によってロータケーシング１２の吸入側から吐出側へ向かう力ｆ４を受ける。力ｆ３とｆ４とはピストン４８に対して互いに逆向きに加わる。   As shown in FIGS. 3 and 4, the piston 48 receives a force f3 from the discharge side to the suction side of the screw rotor 14 by the gas supplied to the forward pressure space s3, and supplies the force to the reverse pressure space s4. The gas f1 receives a force f4 from the suction side toward the discharge side of the rotor casing 12. The forces f3 and f4 are applied to the piston 48 in opposite directions.

さらに、図１及び図２に示すように、吸入ガス通路１５と正方向加圧空間ｓ３とを連通する第３連通路５０が設けられ、吐出ガス通路１９と逆方向加圧空間ｓ４とを連通する第４連通路５２が設けられる。また、第１端面３６が吸入気体の圧力Ｐｓを受ける受圧面の面積と、正方向加圧空間ｓ３におけるピストン４８の受圧面ｐ１の面積が等しくなるように構成され、かつ第２端面３８が吐出気体の圧力Ｐｄを受ける受圧面の面積と、逆方向加圧空間ｓ４におけるピストン４８の受圧面ｐ２の面積が等しくなるように構成されている。
なお、受圧面ｐ２はシリンダロッド２６の端面２６ａも含むことで、吐出ガス通路１９の受圧面の面積と等しくしている。Further, as shown in FIGS. 1 and 2, a third communication passage 50 is provided to communicate the suction gas passage 15 and the forward pressurization space s3, and the discharge gas passage 19 and the reverse pressurization space s4 are communicated. A fourth communication passage 52 is provided. Further, the first end surface 36 is configured such that the area of the pressure receiving surface that receives the pressure Ps of the suction gas is equal to the area of the pressure receiving surface p1 of the piston 48 in the positive pressure space s3, and the second end surface 38 discharges. The area of the pressure receiving surface that receives the gas pressure Pd is equal to the area of the pressure receiving surface p2 of the piston 48 in the reverse pressure space s4.
The pressure receiving surface p <b> 2 includes the end surface 26 a of the cylinder rod 26, thereby making it equal to the area of the pressure receiving surface of the discharge gas passage 19.

上記構成において、正方向加圧空間ｓ３には第３連通路５０を介して吸入ガス通路１５の被圧縮気体Ｇが導入され、逆方向加圧空間ｓ４には第４連通路５２を介して吐出ガス通路１９から被圧縮気体Ｇが導入される。
弁体２２の第１端面３６の受圧面の面積をＡｓｖ１とし、第２端面３８の受圧面の面積をＡｓｖ２とし、ピストン４８の受圧面ｐ１の面積をＡｐ１として、受圧面ｐ２の面積をＡｐ２とする。また、ピストン３０が加圧空間ｓ１及びｓ２から力ｆ１及びｆ２を受ける受圧面の面積は等しいと仮定し、この面積をＡｐ３とする。
この場合、吐出ポート側から吸入ポート側へ向かう向きを正とすると、弁体２２に加わる力Ｆは、次の（１）式で求められる。
Ｆ＝Ｐｄ×Ａｓｖ２−Ｐｓ×Ａｓｖ１＋Ｐｍ×Ａｐ３−Ｐｄ×Ａｐ３＋Ｐｓ×Ａｐ１−Ｐｄ×Ａｐ２ （１）In the above configuration, the compressed gas G of the suction gas passage 15 is introduced into the forward pressurizing space s3 through the third communication passage 50, and discharged into the reverse pressurization space s4 through the fourth communication passage 52. The compressed gas G is introduced from the gas passage 19.
The area of the pressure receiving surface of the first end surface 36 of the valve body 22 is Asv1, the area of the pressure receiving surface of the second end surface 38 is Asv2, the area of the pressure receiving surface p1 of the piston 48 is Ap1, and the area of the pressure receiving surface p2 is Ap2. To do. Further, it is assumed that the areas of the pressure receiving surfaces where the piston 30 receives the forces f1 and f2 from the pressurizing spaces s1 and s2 are equal, and this area is Ap3.
In this case, if the direction from the discharge port side to the suction port side is positive, the force F applied to the valve body 22 is obtained by the following equation (1).
F = Pd * Asv2-Ps * Asv1 + Pm * Ap3-Pd * Ap3 + Ps * Ap1-Pd * Ap2 (1)

式（１）において、Ａｓｖ１＝Ａｐ１及びＡｓｖ２＝Ａｐ２であるので、式（１）は式（２）となる。
Ｆ＝Ｐｍ×Ａｐ３−Ｐｄ×Ａｐ３ （２）
従って、Ｐｍ＝Ｐｄのときに、Ｆ＝０となり、弁体２２は停止する。つまり、弁体２２が停止したとき、スクリュー圧縮機１０の運転効率は最大となる。In Expression (1), Asv1 = Ap1 and Asv2 = Ap2, so Expression (1) becomes Expression (2).
F = Pm * Ap3-Pd * Ap3 (2)
Therefore, when Pm = Pd, F = 0 and the valve body 22 stops. That is, when the valve body 22 stops, the operating efficiency of the screw compressor 10 is maximized.

このように、第１端面３６の受圧面と力ｆ３が加わるピストン４８の受圧面ｐ１とは面積が等しいため、第１端面３６に加わる被圧縮気体Ｇの圧力と力ｆ３とは相殺される。また、第２端面３８の受圧面と力ｆ４が加わるピストン４８の受圧面ｐ２とは面積が等しいため、第２端面３８に加わる被圧縮気体Ｇの圧力と力ｆ４とは相殺される。こうして、弁体２２には、力ｆ１及びｆ２のみ加わることになり、力ｆ１とｆ２との差によって弁体２２はロータ軸方向へ移動する。
本実施形態によれば、弁体２２の第１端面３６及び第２端面３８に加わる被圧縮気体Ｇの圧力を相殺することで、ピストン３０に加わる力ｆ１とｆ２とが等しくなるように、弁体２２のロータ軸方向位置を自動的かつ連続的に最適位置に調整できる。これによって、スクリュー圧縮機１０を常に最も効率良く稼働させることができる。Thus, since the pressure receiving surface p1 of the piston 48 to which the force f3 is applied has the same area as the pressure receiving surface of the first end surface 36, the pressure of the compressed gas G applied to the first end surface 36 and the force f3 are offset. Further, since the pressure receiving surface of the second end surface 38 and the pressure receiving surface p2 of the piston 48 to which the force f4 is applied have the same area, the pressure of the compressed gas G applied to the second end surface 38 and the force f4 are offset. Thus, only the forces f1 and f2 are applied to the valve body 22, and the valve body 22 moves in the rotor axial direction due to the difference between the forces f1 and f2.
According to the present embodiment, by canceling the pressure of the compressed gas G applied to the first end surface 36 and the second end surface 38 of the valve body 22, the force f <b> 1 and f <b> 2 applied to the piston 30 are equalized. The rotor axial position of the body 22 can be automatically and continuously adjusted to the optimum position. Thus, the screw compressor 10 can always be operated most efficiently.

図１及び図２に示す実施形態では、第１連通路３２及び第４連通路５２の一部は、吐出ガス通路１９に連通する１個の主連通路３１で兼用されている。
また、単一のシリンダ２４に仕切り壁５４を設けて第１加圧室２８及び第２加圧室４６を形成している。これに対し、２個のシリンダを設け、一方のシリンダに第１加圧室２８を内蔵させ、他方のシリンダに第２加圧室４６を内蔵させるようにしてもよい。この場合、２個のシリンダは１個のシリンダロッド２６に対して直列に配置され、１個のシリンダロッド２６がこれら２個のシリンダロッドに導設されるようにする。In the embodiment shown in FIGS. 1 and 2, a part of the first communication path 32 and the fourth communication path 52 is shared by one main communication path 31 that communicates with the discharge gas path 19.
Further, the partition wall 54 is provided in the single cylinder 24 to form the first pressurizing chamber 28 and the second pressurizing chamber 46. On the other hand, two cylinders may be provided, the first pressurizing chamber 28 may be built in one cylinder, and the second pressurizing chamber 46 may be built in the other cylinder. In this case, two cylinders are arranged in series with respect to one cylinder rod 26 so that one cylinder rod 26 is led to these two cylinder rods.

一実施形態では、図１及び図４に示すように、第２連通路３４は、弁体２２に形成された中空部５６及びシリンダロッド２６に形成された中空部５７と、弁体２２に形成され吐出直前歯溝空間Ｓｔ２と中空部５６とを連通する第１連通孔５８と、シリンダロッド２６に形成され中空部５７と第１加圧室２８の加圧空間ｓ１とを連通する第２連通孔６０とで構成される。
上記構成によれば、第２連通路３４を弁体２２及びシリンダロッド２６の内部に形成することで、弁体２２及びシリンダロッド２６の外部に第２連通路３４を形成するためのスペースが不要になり、スクリュー圧縮機１０（１０Ａ、１０Ｂ）をコンパクト化できる。In one embodiment, as shown in FIGS. 1 and 4, the second communication passage 34 is formed in the valve body 22 with a hollow portion 56 formed in the valve body 22 and a hollow portion 57 formed in the cylinder rod 26. The first communicating hole 58 that communicates the tooth space immediately before discharge St 2 and the hollow portion 56, and the second communicating hole 58 formed in the cylinder rod 26 and the pressurizing space s 1 of the first pressurizing chamber 28. It is comprised with the communicating hole 60. FIG.
According to the above configuration, the second communication passage 34 is formed inside the valve body 22 and the cylinder rod 26, so that a space for forming the second communication passage 34 outside the valve body 22 and the cylinder rod 26 is unnecessary. Thus, the screw compressor 10 (10A, 10B) can be made compact.

一実施形態では、図２及び図６に示すように、第２連通路３４は、スクリューロータ１４の吐出側端に対面するロータケーシング１２に形成された通路６２を有し、通路６２は吐出直前歯溝空間Ｓｔ２に開口する開口６４を有する。
上記構成によれば、吐出直前歯溝空間Ｓｔ２が吐出ポート１８に最も接近した位置で、吐出直前歯溝空間Ｓｔ２と第２連通路３４とを連通できる。従って、吐出直前歯溝空間Ｓｔ２の被圧縮気体Ｇの圧力を吐出ガス通路１９の吐出気体の圧力に制御するための精度を向上できる。In one embodiment, as shown in FIGS. 2 and 6, the second communication passage 34 has a passage 62 formed in the rotor casing 12 that faces the discharge side end of the screw rotor 14, and the passage 62 is immediately before discharge. It has an opening 64 which opens into the tooth groove space St 2.
According to the above configuration, the tooth space immediately before discharge St 2 and the second communication path 34 can communicate with each other at a position where the tooth space immediately before discharge St 2 is closest to the discharge port 18. Therefore, it is possible to improve the accuracy for controlling the pressure of the compressed gas G of the discharge just before the tooth groove space St 2 to the pressure of the discharge gas of the discharge gas passage 19.

図６には、ロータケーシング１２の内部に雄ロータ１４ａ及び雌ロータ１４ｂが図示されている。図６に示す実施形態では、通路６２は雄ロータ１４ａの吐出側端に対面するロータケーシング１２に形成され、開口６４は雄ロータ側のこのロータケーシング１２に開口する。
また、通路６２はロータケーシング１２の外部に設けられた連通管６６に接続される。連通管６６は、図２に示すように、ロータケーシング１２及びシリンダ２４の隔壁に形成された連通孔６８を介して加圧空間ｓ１に連通する。
例示的な実施形態として、通路６２は雌ロータ１４ｂの吐出側端に対面するロータケーシング１２に形成され、開口６４は雌ロータ側のこのロータケーシング１２に開口する。FIG. 6 shows a male rotor 14 a and a female rotor 14 b inside the rotor casing 12. In the embodiment shown in FIG. 6, the passage 62 is formed in the rotor casing 12 facing the discharge side end of the male rotor 14a, and the opening 64 opens in the rotor casing 12 on the male rotor side.
The passage 62 is connected to a communication pipe 66 provided outside the rotor casing 12. As shown in FIG. 2, the communication pipe 66 communicates with the pressurizing space s <b> 1 through a communication hole 68 formed in the partition of the rotor casing 12 and the cylinder 24.
As an exemplary embodiment, the passage 62 is formed in the rotor casing 12 facing the discharge side end of the female rotor 14b, and the opening 64 opens into the rotor casing 12 on the female rotor side.

一実施形態では、図１に示すように、第１加圧室２８は第２加圧室４６よりスクリューロータ１４の吐出ポート側に位置し、第１加圧室２８に形成される２個の加圧空間ｓ１及びｓ２のうち、第２連通路３４が連通する加圧空間ｓ１は加圧空間ｓ２よりスクリューロータ１４の吐出ポート側に位置する。
上記構成によれば、加圧空間ｓ１を４個の加圧空間ｓ１〜ｓ４の中で吐出ポート１８側へ最も近接して配置でき、これによって、弁体２２及びシリンダロッド２６の内部に形成される中空部５６及び５７を縮小できるため、これら中空部の形成が容易になる。In one embodiment, as shown in FIG. 1, the first pressurizing chamber 28 is positioned closer to the discharge port side of the screw rotor 14 than the second pressurizing chamber 46, and is formed in the first pressurizing chamber 28. Of the pressurizing spaces s1 and s2, the pressurizing space s1 through which the second communication passage 34 communicates is located on the discharge port side of the screw rotor 14 from the pressurizing space s2.
According to the above configuration, the pressurizing space s1 can be disposed closest to the discharge port 18 side among the four pressurizing spaces s1 to s4, and thereby formed inside the valve body 22 and the cylinder rod 26. Since the hollow portions 56 and 57 can be reduced, these hollow portions can be easily formed.

幾つかの実施形態によれば、高コストとなる駆動用機器及び制御用機器を必要とせずに、吐出直前の歯溝空間における被圧縮気体の圧力を圧縮機の吐出圧力と等しくすることで、低コストでスクリュー圧縮機の効率を向上できる。   According to some embodiments, by making the pressure of the compressed gas in the tooth space immediately before discharge equal to the discharge pressure of the compressor without requiring expensive driving equipment and control equipment, The efficiency of the screw compressor can be improved at low cost.

１０（１０Ａ、１０Ｂ） スクリュー圧縮機
１２ ロータケーシング
１４ スクリューロータ
１４ａ 雄ロータ
１４ｂ 雌ロータ
１５ 吸入ガス通路
１６ 吸入ポート
１８ 吐出ポート
１９ 吐出ガス通路
２０ 内部容積比可変弁
２１ 吸入ガス空間
２２ 弁体
２４ シリンダ
２６ シリンダロッド
２８ 第１加圧室
３０、４８ ピストン
３１ 主連通路
３２ 第１連通路
３４ 第２連通路
３６ 第１端面
３８ 第２端面
４０ 切り口
４２ 吸入側端面
４４ 吐出側端面
４６ 第２加圧室
５０ 第３連通路
５２ 第４連通路
５４ 仕切り壁
５６、５７ 中空部
５８ 第１連通孔
６０ 第２連通孔
６２ 通路
６４ 開口
６６ 連通管
６８ 連通孔
Ｇ 被圧縮気体
Ｐｄ 吐出圧力
Ｐｍ 中間圧力
Ｐｓ 吸入圧力
Ｓｔ１ 歯溝空間
Ｓｔ２ 吐出直前歯溝空間
ｐ１、ｐ２ 受圧面10 (10A, 10B) Screw compressor 12 Rotor casing 14 Screw rotor 14a Male rotor 14b Female rotor 15 Suction gas passage 16 Suction port 18 Discharge port 19 Discharge gas passage 20 Internal volume ratio variable valve 21 Suction gas space 22 Valve body 24 Cylinder 26 Cylinder rod 28 First pressurizing chamber 30, 48 Piston 31 Main communication path 32 First communication path 34 Second communication path 36 First end face 38 Second end face 40 Cut end 42 Suction side end face 44 Discharge side end face 46 Second pressurization Chamber 50 Third communication path 52 Fourth communication path 54 Partition wall 56, 57 Hollow portion 58 First communication hole 60 Second communication hole 62 Channel 64 Opening 66 Communication pipe 68 Communication hole G Compressed gas Pd Discharge pressure Pm Intermediate pressure Ps Suction pressure St 1 Gap space St 2 Gap space just before discharge p1, p2 Pressure receiving surface

図１及び図２に示す実施形態では、第１連通路３２及び第４連通路５２の一部は、吐出ガス通路１９に連通する１個の主連通路３１で兼用されている。
また、単一のシリンダ２４に仕切り壁５４を設けて第１加圧室２８及び第２加圧室４６を形成している。これに対し、２個のシリンダを設け、一方のシリンダに第１加圧室２８を内蔵させ、他方のシリンダに第２加圧室４６を内蔵させるようにしてもよい。この場合、２個のシリンダは１個のシリンダロッド２６に対して直列に配置され、１個のシリンダロッド２６がこれら２個のシリンダに導設されるようにする。 In the embodiment shown in FIGS. 1 and 2, a part of the first communication path 32 and the fourth communication path 52 is shared by one main communication path 31 that communicates with the discharge gas path 19.
Further, the partition wall 54 is provided in the single cylinder 24 to form the first pressurizing chamber 28 and the second pressurizing chamber 46. On the other hand, two cylinders may be provided, the first pressurizing chamber 28 may be built in one cylinder, and the second pressurizing chamber 46 may be built in the other cylinder. In this case, the two cylinders are arranged in series with one of the cylinder rod 26, so that one of the cylinder rod 26 is Shirube設these two Cylinders.

Claims (6)

一対の雄ロータ及び雌ロータを含むスクリューロータと、
前記スクリューロータを収容すると共に、被圧縮気体が吸入される吸入ガス通路，吸入ポート及び被圧縮気体が吐出する吐出ポート、吐出ガス通路が形成されるロータケーシングと、
内部容積比を変更可能な内部容積比可変弁と、
を備えるスクリュー圧縮機であって、
前記内部容積比可変弁は、
前記ロータケーシングの内部に設けられ、前記スクリューロータの軸方向に沿って移動可能であり、前記被圧縮気体が前記スクリューロータと前記ロータケーシングとの間に形成される歯溝空間から前記吐出ポートに吐出する吐出位置を規定する弁体と、
少なくとも１個の加圧室を内蔵し、前記弁体に結合され前記スクリューロータの軸方向に沿って配置されたシリンダロッド、及び前記加圧室の内部で前記シリンダロッドに固定され、前記加圧室を前記スクリューロータの軸方向に沿って２個の加圧空間に仕切るピストンを有するシリンダと、
を備え、
さらに、前記吐出ガス通路と前記２個の加圧空間の一方とに連通する第１連通路と、
前記吐出ポートに連通する歯溝空間より１歯溝手前の吐出直前歯溝空間と前記２個の加圧空間の他方とを連通する第２連通路と、
を備えることを特徴とするスクリュー圧縮機。A screw rotor including a pair of male and female rotors;
A rotor casing in which the screw rotor is accommodated, a suction gas passage through which compressed gas is sucked, a suction port, a discharge port through which the compressed gas is discharged, and a discharge gas passage;
An internal volume ratio variable valve capable of changing the internal volume ratio;
A screw compressor comprising:
The internal volume ratio variable valve is:
It is provided inside the rotor casing and is movable along the axial direction of the screw rotor, and the compressed gas is transferred from a tooth space formed between the screw rotor and the rotor casing to the discharge port. A valve body that defines a discharge position to be discharged;
At least one pressurizing chamber is built in, and is connected to the valve body and arranged along the axial direction of the screw rotor, and is fixed to the cylinder rod inside the pressurizing chamber, and the pressurizing chamber A cylinder having a piston partitioning the chamber into two pressurizing spaces along the axial direction of the screw rotor;
With
A first communication passage communicating with the discharge gas passage and one of the two pressurized spaces;
A second communication path that communicates the tooth space immediately before the tooth gap with the other one of the two pressure spaces with respect to the tooth space that communicates with the discharge port;
A screw compressor comprising: 前記２個の加圧空間の一方は前記ピストンに対して前記吸入ポート側に位置し、
前記２個の加圧空間の他方は前記ピストンに対して前記吐出ポート側に位置することを特徴とする請求項１に記載のスクリュー圧縮機。One of the two pressure spaces is located on the suction port side with respect to the piston,
2. The screw compressor according to claim 1, wherein the other of the two pressure spaces is positioned on the discharge port side with respect to the piston. 前記弁体は、前記吸入ガス通路に連通した吸入ガス空間に面した第１端面及び前記吐出ガス通路に面した第２端面を有し、
前記シリンダは、前記スクリューロータの軸方向に沿って配置された第１加圧室及び第２加圧室を内蔵し、
前記第１加圧室において、前記ピストンによって仕切られた前記２個の加圧空間の一方が前記第１連通路に連通すると共に、前記２個の加圧空間の他方が前記第２連通路に連通し、
前記第２加圧室において、前記ピストンによって仕切られた前記２個の加圧空間のうち、前記ピストンを前記吐出ポート側から前記吸入ポート側へ加圧する正方向加圧空間と前記吸入ガス通路とを連通する第３連通路と、
前記第２加圧室に形成される前記２個の加圧空間のうち、前記ピストンを前記吸入ポート側から前記吐出ポート側へ加圧する逆方向加圧空間と前記吐出ガス通路とを連通する第４連通路と、
を備え、
前記第１端面が前記吸入ガス空間の前記被圧縮気体から加圧される受圧面と前記正方向加圧空間における前記ピストンの受圧面の面積が等しく、かつ前記第２端面が前記吐出ガス通路の前記被圧縮気体から加圧される受圧面と前記逆方向加圧空間における前記ピストンの受圧面の面積が等しいことを特徴とする請求項１又は２に記載のスクリュー圧縮機。The valve body has a first end surface facing an intake gas space communicating with the intake gas passage and a second end surface facing the discharge gas passage,
The cylinder includes a first pressurizing chamber and a second pressurizing chamber disposed along the axial direction of the screw rotor,
In the first pressurizing chamber, one of the two pressurizing spaces partitioned by the piston communicates with the first communicating path, and the other of the two pressurizing spaces communicates with the second communicating path. Communication,
In the second pressurizing chamber, of the two pressurizing spaces partitioned by the piston, a positive pressurizing space for pressurizing the piston from the discharge port side to the suction port side, and the suction gas passage, A third communication passage that communicates with each other;
Of the two pressurization spaces formed in the second pressurization chamber, a reverse pressurization space for pressurizing the piston from the suction port side to the discharge port side and a discharge gas passage communicate with each other. 4 passages,
With
The area of the pressure receiving surface where the first end surface is pressurized from the compressed gas in the suction gas space and the pressure receiving surface of the piston in the positive direction pressure space are equal, and the second end surface is the discharge gas passage. The screw compressor according to claim 1 or 2, wherein the pressure receiving surface pressurized from the compressed gas and the pressure receiving surface of the piston in the reverse pressure space have the same area. 前記第２連通路は、
前記弁体及び前記シリンダロッドに形成された中空部と、
前記弁体に形成され前記吐出直前歯溝空間と前記中空部とを連通する第１連通孔と、
前記シリンダロッドに形成され前記中空部と前記２個の加圧空間の他方とを連通する第２連通孔と、
で構成されることを特徴とする請求項１乃至３の何れか１項に記載のスクリュー圧縮機。The second communication path is
A hollow portion formed in the valve body and the cylinder rod;
A first communication hole formed in the valve body and communicating with the tooth space immediately before discharge and the hollow portion;
A second communication hole formed in the cylinder rod and communicating the hollow portion and the other of the two pressure spaces;
The screw compressor according to any one of claims 1 to 3, wherein the screw compressor is configured as follows. 前記第２連通路は、前記スクリューロータの吐出側端に対面する前記ロータケーシングに形成された通路を有し、前記通路は前記ロータケーシングの壁面から前記吐出直前歯溝空間に開口する開口を有することを特徴とする請求項１乃至３の何れか１項に記載のスクリュー圧縮機。   The second communication passage has a passage formed in the rotor casing facing the discharge side end of the screw rotor, and the passage has an opening that opens from the wall surface of the rotor casing to the tooth space immediately before discharge. The screw compressor according to any one of claims 1 to 3, wherein the screw compressor is provided. 前記シリンダは、前記スクリューロータの軸方向に沿って配置された第１加圧室及び第２加圧室を内蔵し、
前記第１加圧室は前記第２加圧室より前記スクリューロータの吐出ポート側に位置し、
前記第１加圧室に形成される前記２個の加圧空間のうち、前記第２連通路が連通する前記２個の加圧空間の他方は前記２個の加圧空間の一方より前記吐出ポート側に位置することを特徴とする請求項１乃至５の何れか一項に記載のスクリュー圧縮機。The cylinder includes a first pressurizing chamber and a second pressurizing chamber disposed along the axial direction of the screw rotor,
The first pressurizing chamber is located on the discharge port side of the screw rotor from the second pressurizing chamber,
Of the two pressurization spaces formed in the first pressurization chamber, the other of the two pressurization spaces communicated with the second communication path is discharged from one of the two pressurization spaces. The screw compressor according to any one of claims 1 to 5, wherein the screw compressor is located on a port side.
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