JPS642795B2 - - Google Patents
Info
- Publication number
- JPS642795B2 JPS642795B2 JP14882981A JP14882981A JPS642795B2 JP S642795 B2 JPS642795 B2 JP S642795B2 JP 14882981 A JP14882981 A JP 14882981A JP 14882981 A JP14882981 A JP 14882981A JP S642795 B2 JPS642795 B2 JP S642795B2
- Authority
- JP
- Japan
- Prior art keywords
- pressure
- rotor
- discharge side
- suction side
- male
- Prior art date
- Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
- Expired
Links
- 230000001105 regulatory effect Effects 0.000 claims description 13
- 239000012530 fluid Substances 0.000 claims description 8
- 230000006835 compression Effects 0.000 description 15
- 238000007906 compression Methods 0.000 description 15
- 238000010586 diagram Methods 0.000 description 3
- 230000002093 peripheral effect Effects 0.000 description 3
- 238000000034 method Methods 0.000 description 2
- 230000005540 biological transmission Effects 0.000 description 1
- 230000000694 effects Effects 0.000 description 1
Classifications
-
- 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
- F04C29/00—Component parts, details or accessories of pumps or pumping installations, not provided for in groups F04C18/00 - F04C28/00
- F04C29/0021—Systems for the equilibration of forces acting on the pump
Landscapes
- Engineering & Computer Science (AREA)
- Mechanical Engineering (AREA)
- General Engineering & Computer Science (AREA)
- Rotary-Type Compressors (AREA)
Description
【発明の詳細な説明】
本発明は、スクリユ圧縮機のスラスト方向の力
のつり合い装置に関する。DETAILED DESCRIPTION OF THE INVENTION The present invention relates to a force balancing device in the thrust direction of a screw compressor.
第１図はスクリユ圧縮機の雄，雌ロータと、そ
の軸受と、回転駆動用のギアとを示す。 FIG. 1 shows the male and female rotors of a screw compressor, their bearings, and gears for rotational driving.
スクリユ圧縮機の雄，雌ロータ１，２は、ケー
シング（第１図中では省略）の内部に収容され、
雄ロータ１はシヤフト３の両端部において軸受
５，７，７′により支持され、雌ロータ２はシヤ
フト４の両端部で軸受６，８，８′により支持さ
れている。 The male and female rotors 1 and 2 of the screw compressor are housed inside a casing (not shown in Figure 1).
The male rotor 1 is supported at both ends of the shaft 3 by bearings 5, 7, 7', and the female rotor 2 is supported at both ends of the shaft 4 by bearings 6, 8, 8'.
前記雄ロータ１のシヤフト３の一端部にはギア
９が設けられ、他端部にはギア１０が設けられて
おり、一方雌ロータ２のシヤフト４の他端部には
ギア１１が設けられている。 A gear 9 is provided at one end of the shaft 3 of the male rotor 1 and a gear 10 is provided at the other end, while a gear 11 is provided at the other end of the shaft 4 of the female rotor 2. There is.
前記雄ロータ１のシヤフト３の一端部に設けら
れたギア９は、回転駆動装置（図示省略）より動
力を受けて雄ロータ１を駆動し、雄ロータ１のシ
ヤフト３の他端部と雌ロータ２のシヤフト４の他
端部とに設けられたギア１０，１１は、一対のタ
イミングギアを構成していて雌ロータ２を雄ロー
タ１と同期駆動させるようになつている。これら
のギア９，１０，１１には動力伝達を滑らかにす
るため、ヘリカルギアが使用されており、このた
めギアのねじれ方向によつて設定された方向にス
ラスト力が発生する。そして、スクリユ圧縮機で
はギア９，１０，１１のうち、ギア９，１０によ
るスラスト力は全負荷時の圧縮反力を軽減するた
め、吸入側から吐出側に作用するように、またギ
ア１１によるスラスト力はギア１０の反力により
吐出側から吸入側に作用するように、ねじれ方向
が決められている。 A gear 9 provided at one end of the shaft 3 of the male rotor 1 drives the male rotor 1 by receiving power from a rotary drive device (not shown), and connects the other end of the shaft 3 of the male rotor 1 with the female rotor. Gears 10 and 11 provided at the other end of the second shaft 4 constitute a pair of timing gears, and drive the female rotor 2 in synchronization with the male rotor 1. These gears 9, 10, and 11 are helical gears for smooth power transmission, and therefore thrust force is generated in a direction set by the twist direction of the gears. In the screw compressor, among the gears 9, 10, and 11, the thrust force from gears 9 and 10 is applied from the suction side to the discharge side in order to reduce the compression reaction force at full load. The twisting direction of the thrust force is determined so that it acts from the discharge side to the suction side due to the reaction force of the gear 10.
また、雄，雌両ロータ１，２は、圧縮ガスの圧
縮反力により常に吐出側から吸入側へ押す力を受
けている。ただし、吸入圧が通常２Kg／cm2Ｇ程度
で使用されるような、２段圧縮機の２段側に使用
されるような場合は、無負荷運転開始時、吐出側
が大気圧になり、吸込側が２Kg／cm2Ｇ程度で、そ
の差圧により吸入側から吐出側へロータを押す力
が一時的に働くこともある。この状態は、吸入側
の絞り弁を閉じることにより吸入側の圧力が大気
圧以下になると、吐出側から吸入側へロータを押
す力に転換される。その結果、雌ロータ２は第１
図に矢印ロで示されるギア反力と、矢印ニで示さ
れる圧縮反力との、吐出側から吸入側に向かう同
じ方向の力を受けているので、安定した状態に保
たれている。 Further, both the male and female rotors 1 and 2 are always subjected to a force pushing them from the discharge side to the suction side due to the compression reaction force of the compressed gas. However, when used on the second stage side of a two-stage compressor, where the suction pressure is normally around 2 kg/cm 2 G, the discharge side becomes atmospheric pressure at the start of no-load operation, and the suction The pressure difference on the side is about 2 kg/cm 2 G, and the force that pushes the rotor from the suction side to the discharge side may work temporarily due to the pressure difference. This state is converted into a force that pushes the rotor from the discharge side to the suction side when the pressure on the suction side becomes below atmospheric pressure by closing the throttle valve on the suction side. As a result, the female rotor 2
It is maintained in a stable state because it receives force in the same direction from the discharge side to the suction side, which is the gear reaction force shown by the arrow B in the figure and the compression reaction force shown by the arrow D.
一方、雄ロータ１は第１図に矢印イで示される
吸入側から吐出側に作用するギア反力と、矢印ハ
で示されるように、吐出側から吸入側に作用する
圧縮反力とを受けている。このため、圧縮機の全
負荷時にはギア反力が圧縮反力によるスラスト力
を減少させた状態で雄ロータ１を吐出側から吸入
側へ移動させるが、圧縮機の起動時および無負荷
時には吐出側を大気に開放するため、吸入側と吐
出側との圧力差が少なく、ギア反力が圧縮反力に
打ち勝ち、雄ロータ１を吐出側へ移動させるよう
に作用する。したがつて、雄ロータ１は圧縮機の
運転状態によつて方向および大きさの異なる力を
受ける結果、不安定な状態におかれる。 On the other hand, the male rotor 1 receives a gear reaction force acting from the suction side to the discharge side, as shown by arrow A in FIG. 1, and a compression reaction force acting from the discharge side to the suction side, as shown by arrow C. ing. Therefore, when the compressor is fully loaded, the gear reaction force moves the male rotor 1 from the discharge side to the suction side while reducing the thrust force due to the compression reaction force, but when the compressor is started up or under no load, the male rotor 1 is moved from the discharge side to the suction side. Since it is open to the atmosphere, the pressure difference between the suction side and the discharge side is small, and the gear reaction force overcomes the compression reaction force and acts to move the male rotor 1 toward the discharge side. Therefore, the male rotor 1 is placed in an unstable state as a result of being subjected to forces that differ in direction and magnitude depending on the operating state of the compressor.
これに対して、従来、圧縮機の全負荷時の圧縮
反力を軽減するため、ロータの軸端部にピストン
を設け、これに圧力をかけ、圧縮反力と反対方向
の力を発生させる技術が提案されている。 Conventionally, in order to reduce the compression reaction force when the compressor is at full load, a piston is installed at the end of the rotor shaft, and pressure is applied to this piston to generate a force in the opposite direction to the compression reaction force. is proposed.
しかし、前記従来技術によると、圧縮機の起動
時あるいは無負荷時の圧縮反力が小さい状態と、
圧縮反力が大きい全負荷時とで、ロータの軸方向
荷重の向きが変わるので、ロータの軸方向の挙動
を安定化できない欠点がある。 However, according to the prior art, the compression reaction force is small when the compressor is started or when there is no load;
Since the direction of the axial load on the rotor changes between when the compressive reaction force is large and the load is full, there is a drawback that the axial behavior of the rotor cannot be stabilized.
本発明の目的は、圧縮機の起動時，全負荷時お
よび無負荷時に至る全運転状態にわたつて油圧源
からの圧油によりロータに、吐出側から吸入側方
向に一定の力を連続的に付与しうるスクリユ圧縮
機のスラスト力のつり合い装置を供旧するにあ
る。 The object of the present invention is to continuously apply a constant force to the rotor from the discharge side to the suction side using pressure oil from the hydraulic source over all operating conditions of the compressor, from startup to full load to no load. The purpose of this project is to supply and replace a device for balancing the thrust force of a screw compressor.
本発明の特徴は、ロータの軸端部にバランスピ
ストンと、該バランスピストンを摺動自在に嵌挿
するとともに、該バランスピストンにより第１，
第２のチヤンバを形成するシリンダとからなるス
ラスト付与手段を設け、該スラスト付与手段の第
１，第２のチヤンバを流体圧回路を介して油圧源
に接続し、該流体圧回路に前記圧縮機の吸入側圧
力および吐出側圧力により切換操作して、油圧源
からの圧油を前記第１のチヤンバあるいは第２の
チヤンバに供給する油圧調整弁を備えたところに
あり、この構成により前記目的を確実に達成する
ことができたものである。 The present invention is characterized in that a balance piston is slidably inserted into the shaft end of the rotor, and the balance piston allows the first
and a cylinder forming a second chamber, the first and second chambers of the thrust applying means are connected to a hydraulic power source via a fluid pressure circuit, and the compressor is connected to the fluid pressure circuit. The device is equipped with a hydraulic pressure regulating valve that supplies pressure oil from the hydraulic source to the first chamber or the second chamber by switching operation according to the suction side pressure and the discharge side pressure of the hydraulic pressure source. This was definitely achievable.
以下、本発明を図面に基づいて説明する。 Hereinafter, the present invention will be explained based on the drawings.
第２図，第３図および第４図は、スクリユ圧縮
機と本発明つり合い装置の一実施例を示す。 2, 3 and 4 show an embodiment of the screw compressor and the balancing device of the present invention.
そのスクリユ圧縮機は、第２図に示されるよう
に、ケーシング１２、これの内部に収容された
雄，雌ロータ１３，１４、雄ロータ１３のシヤフ
ト１５の軸受１７，１９，１９′，２１，２１′、
雌ロータ１４のシヤフト１６の軸受１８，２０，
２０′、雄ロータ１３のシヤフト１５の一端部に
設けられたギア２２と他端部に設けられたギア２
３，雌ロータ１４のシヤフト１６に設けられたギ
ア２４とを備えている。 As shown in FIG. 2, the screw compressor consists of a casing 12, male and female rotors 13, 14 housed inside the casing, bearings 17, 19, 19', 21 of the shaft 15 of the male rotor 13, 21′,
Bearings 18, 20 of the shaft 16 of the female rotor 14,
20', a gear 22 provided at one end of the shaft 15 of the male rotor 13 and a gear 2 provided at the other end;
3, a gear 24 provided on the shaft 16 of the female rotor 14.
前記ケーシング１２には、雄，雌ロータ１３，
１４の一端部側に吸入口が形成され、他端部側に
は吐出口が形成されているが、吸入口，吐出口と
も図面では省略されている。 The casing 12 includes male and female rotors 13,
A suction port is formed at one end of the 14, and a discharge port is formed at the other end, but both the suction port and the discharge port are omitted in the drawing.
前記雄ロータ１３のシヤフト１５の一端部に設
けられたギア２２は回転駆動装置（図示省略）よ
り動力を受けて雄ロータ１３を駆動し、雄ロータ
１３のシヤフト１５の他端部と雌ロータ１４のシ
ヤフト１６の他端部とに設けられたギア２３，２
４は、互いにかみ合う一対のタイミングギアを構
成していて雌ロータ１４を雄ロータ１３と同規駆
動しうるようになつている。これらのギア２２，
２３，２４には、ヘリカルギアが用いられてい
る。 A gear 22 provided at one end of the shaft 15 of the male rotor 13 receives power from a rotary drive device (not shown) to drive the male rotor 13, and connects the other end of the shaft 15 of the male rotor 13 and the female rotor 14. Gears 23, 2 provided at the other end of the shaft 16
Reference numeral 4 constitutes a pair of timing gears that mesh with each other so that the female rotor 14 can be driven in the same direction as the male rotor 13. These gears 22,
Helical gears are used for 23 and 24.
前記つり合い装置は、スタフイングボツクス２
５に設けられたバランスピストン２７、エンドカ
バー２６に形成されたシリンダ２８、該シリンダ
２８内の第１，第２のチヤンバ２９，３０の圧力
を調整する流体圧回路３８とを備えている。 The balancing device includes stuffing box 2.
5, a cylinder 28 formed in the end cover 26, and a fluid pressure circuit 38 that adjusts the pressure in the first and second chambers 29, 30 within the cylinder 28.
前記スタフイングボツクス２５には、雄ロータ
１４のシヤフト１５の他端部に２個並設された軸
受２１，２１′が収容されており、このスタフイ
ングボツクス２５の外周面にバランスピストン２
７がリング状に設けられている。 The stuffing box 25 accommodates two bearings 21 and 21' arranged in parallel at the other end of the shaft 15 of the male rotor 14, and a balance piston 2 is mounted on the outer peripheral surface of the stuffing box 25.
7 is provided in a ring shape.
前記エンドカバー２６は、ケーシング１２の他
端部に固定され、スラスト付与手段が形成されて
いる。該スラスト付与手段は、シリンダ２８と、
該シリンダ２８内を摺動自在に嵌挿する前記バラ
ンスピストン２７とから構成され、該シリンダ２
８の内部はバランスピストン２７により第１，第
２のチヤンバ２９，３０に区画されている。前記
第１，第２のチヤンバ２９，３０には、各別に連
通するポート３１，３２が形成されている。 The end cover 26 is fixed to the other end of the casing 12 and forms thrust applying means. The thrust applying means includes a cylinder 28;
and the balance piston 27 that is slidably inserted into the cylinder 28.
8 is divided into first and second chambers 29 and 30 by a balance piston 27. The first and second chambers 29 and 30 are respectively formed with ports 31 and 32 that communicate with each other.
なお、前記アウタリング２５の外周面の両端部
とエンドカバー２６の内周面間にはＯリング３３
が介装され、バランスピストン２７の外周面とシ
リンダ２８の内周面間にはＯリング３４が介装さ
れている。 Note that an O-ring 33 is provided between both ends of the outer circumferential surface of the outer ring 25 and the inner circumferential surface of the end cover 26.
An O-ring 34 is interposed between the outer peripheral surface of the balance piston 27 and the inner peripheral surface of the cylinder 28.
また、第４図に示されるように、スクリユ圧縮
機の吸入口には絞り弁３５が接続され、吐出口に
は吐出開放弁３６と逆止弁３７とが連結されてい
る。 Further, as shown in FIG. 4, a throttle valve 35 is connected to the suction port of the screw compressor, and a discharge release valve 36 and a check valve 37 are connected to the discharge port.
前記流体圧回路３８には、この実施例では油圧
回路が採用されている。そして、この流体圧回路
３８は第４図に示されるように、オイルタンク３
９，オイルポンプ４０および第１，第２の油圧調
整弁４１，４２とを配備している。前記第１，第
２の油圧調整弁４１，４２には、それぞれバイパ
ス弁（図示省略）が内蔵されている。また、第
１，第２の油圧調整弁４１，４２は往き側配管４
３を介してオイルポンプ４０に並列に接続されて
いる。一方、第１の油圧調整弁４１は帰り側配管
４４を介してオイルタンク３９に連通され、他の
配管４６を介して前記シリンダ２８内の第１のチ
ヤンバ２９のポート３１に接続されており、また
第１の油圧調整弁４１には圧縮機の吸入側の圧力
が操作信号４８として挿入されている。他方、第
２の油圧調整弁４２は帰り側配管４５を通じてオ
イルタンク３９に連通され、他の配管４７を介し
て前記シリンダ２８内の第２のチヤンバ３０のポ
ート３２に接続され、また第２の油圧調整弁４２
には圧縮機の吐出側の圧力が操作信号４９として
挿入されている。 In this embodiment, a hydraulic circuit is employed as the fluid pressure circuit 38. This fluid pressure circuit 38 is connected to the oil tank 3 as shown in FIG.
9, an oil pump 40 and first and second oil pressure regulating valves 41 and 42 are provided. The first and second oil pressure regulating valves 41 and 42 each have a built-in bypass valve (not shown). Further, the first and second hydraulic pressure regulating valves 41 and 42 are connected to the outgoing side piping 4.
3 in parallel to the oil pump 40. On the other hand, the first oil pressure regulating valve 41 is communicated with the oil tank 39 via a return pipe 44, and is connected to the port 31 of the first chamber 29 in the cylinder 28 via another pipe 46, Further, the pressure on the suction side of the compressor is inserted into the first oil pressure regulating valve 41 as an operation signal 48 . On the other hand, the second oil pressure regulating valve 42 is communicated with the oil tank 39 through a return pipe 45, is connected to the port 32 of the second chamber 30 in the cylinder 28 through another pipe 47, and is connected to the port 32 of the second chamber 30 in the cylinder 28. Hydraulic adjustment valve 42
The pressure on the discharge side of the compressor is inserted as an operation signal 49.
前記実施例のスラスト力のつり合い装置につ
き、第４図，第５図に関連して作用を説明する。 The operation of the thrust force balancing device of the above embodiment will be explained with reference to FIGS. 4 and 5.
圧縮機の起動時には、絞り弁３５は一般に閉じ
られ、吐出開放弁３６が開かれ、吐出側が大気に
開放されるが、起動直後は、吸入側，吐出側とも
大気圧であるため、吸入側と吐出側との圧力差が
なく、ギア反力により雄ロータ１３には吸入側か
ら吐出側へ移動させる力が働くので、第１の油圧
調整弁４１配管４６およびポート３２を通じてシ
リンダ２８内の第２のチヤンバ３０に圧力をか
け、雄ロータ１３には吐出側から吸入側へ押す力
を付与する。 When the compressor is started, the throttle valve 35 is generally closed and the discharge release valve 36 is opened, opening the discharge side to the atmosphere. However, immediately after startup, both the suction side and the discharge side are at atmospheric pressure, so the suction side and the discharge side are both at atmospheric pressure. Since there is no pressure difference with the discharge side and the gear reaction force acts on the male rotor 13 to move it from the suction side to the discharge side, the second Pressure is applied to the chamber 30 of the pump, and a force is applied to the male rotor 13 to push it from the discharge side to the suction side.
圧縮機の全負荷時には、ガスは絞り弁３５を通
つて雄，雌ロータ１３，１４に送られ、該雄，雌
ロータ３，１４で圧縮され、その圧縮ガスは逆止
弁３７を通つて使用に供される。この状態では、
吐出開放弁３６は閉じられている。また、この全
負荷時には圧縮ガスによる圧縮反力が大きくなつ
て、該圧縮反力はギア反力により軽減されるもの
の、圧縮反力がギア反力に打ち勝ち、雄ロータ１
３を吐出側から吸入側へ移動させる力が働くの
で、第２の油圧調整弁４２、配管４７およびポー
ト３１を通じてシリンダ２８内の第１のチヤンバ
２９に圧力をかけ、雄ロータ１３を吐出側から吸
入側へ押す力を適正に保持する。 When the compressor is at full load, gas is sent through the throttle valve 35 to the male and female rotors 13 and 14, compressed by the male and female rotors 3 and 14, and the compressed gas is used through the check valve 37. served. In this state,
The discharge release valve 36 is closed. In addition, at this full load, the compression reaction force due to the compressed gas increases, and although this compression reaction force is reduced by the gear reaction force, the compression reaction force overcomes the gear reaction force, and the male rotor 1
3 from the discharge side to the suction side, pressure is applied to the first chamber 29 in the cylinder 28 through the second oil pressure regulating valve 42, piping 47 and port 31, and the male rotor 13 is moved from the discharge side. Maintain appropriate force to push toward the suction side.
圧縮機が全負荷運転から無負荷運転に入ると、
吐出開放弁３６が開かれ、吐出側が大気圧まで低
下される。この過程で雄ロータ１３に働く吐出側
から吸入側へ押す力が小さくなる。この場合に
は、吐出側の圧力による操作信号４９によつて第
２の油圧調整弁４２に内蔵されたバイパス弁が開
かれ、第１のチヤンバ２９内の圧力がポート３
１、配管４６および帰り側配管４４を通じてオイ
ルタンク３９に逃がされ、第１のチヤンバ２９の
圧力が下げられるため、雄ロータ１３を吐出側か
ら吸入側に押す力が一定に保たれる。ついで、絞
り弁３５が閉じられると、吸入側の圧力が真空に
低下し、雄ロータ１３を吐出側から吸入側に押す
力が大きくなる。この場合には、吸入側の圧力に
よる操作信号４８によつて第１の油圧調整弁４１
に内蔵されたバイパス弁が開かれ、第２チヤンバ
３０の圧力がポート３２、配管４７および帰り側
配管４５を通じてオイルタンク３９に逃がされる
ので、雄ロータ１３を吐出側から吸入側へ押す力
が一定に保たれる。 When the compressor goes from full load operation to no load operation,
The discharge release valve 36 is opened and the pressure on the discharge side is lowered to atmospheric pressure. In this process, the force acting on the male rotor 13 that pushes it from the discharge side to the suction side becomes smaller. In this case, the bypass valve built in the second hydraulic pressure regulating valve 42 is opened by the operation signal 49 based on the pressure on the discharge side, and the pressure in the first chamber 29 is reduced to the port 3.
1. Since the oil is released to the oil tank 39 through the piping 46 and the return piping 44 and the pressure in the first chamber 29 is lowered, the force pushing the male rotor 13 from the discharge side to the suction side is kept constant. Next, when the throttle valve 35 is closed, the pressure on the suction side is reduced to vacuum, and the force pushing the male rotor 13 from the discharge side to the suction side increases. In this case, the first hydraulic pressure regulating valve 41 is controlled by the operation signal 48 based on the suction side pressure.
The built-in bypass valve is opened, and the pressure in the second chamber 30 is released to the oil tank 39 through the port 32, piping 47, and return piping 45, so the force pushing the male rotor 13 from the discharge side to the suction side is constant. is maintained.
圧縮機が無負荷時から全負荷時に移動する場合
には、前記と全く逆の過程をたどり、吸入側，吐
出側の圧力を操作信号４８，４９として第１，第
２の油圧調整弁４１，４２が操作され、第１、第
２のチヤンバ４１，４２内の圧力が高められ、第
５図に示されるように、雄ロータ１３を吐出側か
ら吸入側へ押す力が一定に保たれる。 When the compressor moves from a no-load state to a full-load state, the process is completely reverse to that described above, and the pressures on the suction side and the discharge side are used as operation signals 48 and 49 to operate the first and second hydraulic pressure regulating valves 41, 49, 42 is operated, the pressure in the first and second chambers 41 and 42 is increased, and as shown in FIG. 5, the force pushing the male rotor 13 from the discharge side to the suction side is kept constant.
以上の作用により、雄ロータ１３を圧縮機の全
運転状態にわたつて、第５図に示されるように、
ギア反力と圧縮反力とバランスピストン２７に加
わる圧力であるピストン力との和が、常に吐出側
から吸入側へ一定の力で押すように調整されるの
で、雄ロータ１３の挙動を安定化できる。 As a result of the above-mentioned action, the male rotor 13 is operated over all operating conditions of the compressor, as shown in FIG.
The sum of the gear reaction force, the compression reaction force, and the piston force, which is the pressure applied to the balance piston 27, is adjusted so that it always pushes from the discharge side to the suction side with a constant force, so the behavior of the male rotor 13 is stabilized. can.
なお、この実施例では雌ロータ１４はギア２４
によるギア反力と圧縮ガスによる圧縮反力との作
用で吐出側から吸入側へ押されているので、挙動
不安定の問題は生じない。 In addition, in this embodiment, the female rotor 14 has a gear 24.
Since it is pushed from the discharge side to the suction side by the action of the gear reaction force caused by the gas and the compression reaction force caused by the compressed gas, the problem of unstable behavior does not occur.
また、前記第１，第２の油圧調整弁４１，４２
の操作信号は、吸入側と吐出側の圧力に限らず、
第３図に示されるように、雄ロータ１３のシヤフ
ト１５にひずみゲージ５０を組み込み、該ひずみ
ゲージ５０からの信号により操作するようにして
もよい。 Further, the first and second oil pressure regulating valves 41 and 42
The operation signal is not limited to the pressure on the suction side and discharge side.
As shown in FIG. 3, a strain gauge 50 may be incorporated into the shaft 15 of the male rotor 13 and operated by signals from the strain gauge 50.
さらにまた、図示実施例では雄ロータ１３のシ
ヤフト１５にのみバランスピストンを取り付けた
場合を示しているが、雌ロータ１４のシヤフト１
６にもバランスピストンを取り付け、両方のバラ
ンスピストンによりロータを吐出側から吸入側へ
一定の力で押すようにしてもよい。 Furthermore, although the illustrated embodiment shows a case where the balance piston is attached only to the shaft 15 of the male rotor 13, the balance piston is attached only to the shaft 15 of the female rotor 14.
6 may also be equipped with a balance piston, and both balance pistons may push the rotor from the discharge side to the suction side with a constant force.
本発明は、以上説明した構成，作用のもので、
本発明によれば、圧縮機の起動時、全負荷時およ
び無負荷時に至る全運転時にわたつてロータを吐
出側から吸入側へ、常に一定の力で連続的に押し
ているので、ロータの挙動を安定化でき、ロータ
のシヤフトの軸受に加わる荷重の方向、大きさと
も一定になしうる結果、圧縮機を長期間にわたつ
て高性能に維持できる効果がある。 The present invention has the configuration and operation described above,
According to the present invention, the rotor is continuously pushed with a constant force from the discharge side to the suction side during the entire operation of the compressor, from startup to full load to no load, so the behavior of the rotor can be controlled. The load can be stabilized and the direction and magnitude of the load applied to the rotor shaft bearing can be kept constant, which has the effect of maintaining high performance of the compressor over a long period of time.
第１図はスクリユ圧縮機の概略説明図、第２図
はスクリユ圧縮機と本発明のつり合い装置の一例
を示す横断平面図、第３図はつり合い装置部分の
拡大断面図、第４図はつり合い装置を吸入側と吐
出側の圧力を操作信号として作動させる実施例の
系統図、第５図は本発明におけるギア反力と圧縮
反力と、ピストン力と、ロータに働く力との関係
を示す線図である。
１２……ハウジング、１３，１４……雄、雌ロ
ータ、１５，１６……雄，雌ロータのシヤフト、
１７，１８，１９，１９′，２０，２０′，２１，
２１′……軸受、２２〜２４……ギア、２７……
バランスピストン、２８……シリンダ、２９，３
０……第１、第２のチヤンバ、３１，３２……第
１、第２のチヤンバのポート、３８……流体圧回
路。
Fig. 1 is a schematic explanatory diagram of a screw compressor, Fig. 2 is a cross-sectional plan view showing an example of the screw compressor and the balancing device of the present invention, Fig. 3 is an enlarged cross-sectional view of the balancing device portion, and Fig. 4 is the balancing device. A system diagram of an embodiment in which the device is operated using pressures on the suction side and the discharge side as operation signals, and FIG. 5 shows the relationship between gear reaction force, compression reaction force, piston force, and force acting on the rotor in the present invention. It is a line diagram. 12...Housing, 13, 14...Male and female rotors, 15, 16...Male and female rotor shafts,
17, 18, 19, 19', 20, 20', 21,
21'...Bearing, 22-24...Gear, 27...
Balance piston, 28...Cylinder, 29,3
0...First and second chambers, 31, 32...Ports of first and second chambers, 38...Fluid pressure circuit.
Claims (1)
し、該一対の雄、雌ロータの回転によつて吸入側
から吸入した気体を圧縮して吐出側から吐出する
スクリユ圧縮機において、前記一対の雄、雌ロー
タ軸端部にバランスピストンと、該バランスピス
トンを摺動自在に嵌挿するとともに、該バランス
ピストンにより第１、第２のチヤンバを形成する
シリンダとからなるスラスト付与手段を設け、該
スラスト付与手段の第１、第２のチヤンバを流体
圧回路を介して油圧源に接続し、該流体圧回路に
前記圧縮機の吸入側圧力および吐出側圧力により
切換操作して、油圧源からの圧油を前記第１のチ
ヤンバあるいは第２のチヤンバに供給する油圧調
整弁を備えていることを特徴とするスクリユ圧縮
機のスラスト力のつり合い装置。1. A screw compressor that houses a pair of male and female rotors in a casing and compresses gas sucked in from the suction side by rotation of the pair of male and female rotors and discharges it from the discharge side. A thrust imparting means is provided at the end of the female rotor shaft, and includes a balance piston and a cylinder into which the balance piston is slidably inserted and which forms first and second chambers with the balance piston. The first and second chambers of the application means are connected to a hydraulic power source via a fluid pressure circuit, and the pressure from the hydraulic power source is applied to the fluid pressure circuit by switching the pressure on the suction side and the pressure on the discharge side of the compressor. A thrust force balancing device for a screw compressor, comprising a hydraulic pressure regulating valve for supplying oil to the first chamber or the second chamber.
Priority Applications (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14882981A JPS5851290A (en) | 1981-09-22 | 1981-09-22 | Thrust force balancing apparatus for screw compressor |
Applications Claiming Priority (1)
| Application Number | Priority Date | Filing Date | Title |
|---|---|---|---|
| JP14882981A JPS5851290A (en) | 1981-09-22 | 1981-09-22 | Thrust force balancing apparatus for screw compressor |
Publications (2)
| Publication Number | Publication Date |
|---|---|
| JPS5851290A JPS5851290A (en) | 1983-03-25 |
| JPS642795B2 true JPS642795B2 (en) | 1989-01-18 |
Family
ID=15461652
Family Applications (1)
| Application Number | Title | Priority Date | Filing Date |
|---|---|---|---|
| JP14882981A Granted JPS5851290A (en) | 1981-09-22 | 1981-09-22 | Thrust force balancing apparatus for screw compressor |
Country Status (1)
| Country | Link |
|---|---|
| JP (1) | JPS5851290A (en) |
Families Citing this family (6)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| JPS5877190A (en) * | 1981-11-02 | 1983-05-10 | Hitachi Ltd | Device for preventing shaft vibration in screw fluid machine |
| JPS59213962A (en) * | 1983-05-20 | 1984-12-03 | Hokuetsu Kogyo Co Ltd | Rotary compressor |
| FR2567568B1 (en) * | 1984-07-16 | 1988-11-10 | Worthington Turbodyne | ROTATING MACHINE WITH ROTATING BALANCING AND PRELOADING PISTON |
| JPH0792065B2 (en) * | 1990-06-30 | 1995-10-09 | 株式会社神戸製鋼所 | Screw compressor |
| US5135374A (en) * | 1990-06-30 | 1992-08-04 | Kabushiki Kaisha Kobe Seiko Sho | Oil flooded screw compressor with thrust compensation control |
| WO2015140986A1 (en) * | 2014-03-20 | 2015-09-24 | 住友精密工業株式会社 | Hydraulic device |
Family Cites Families (2)
| Publication number | Priority date | Publication date | Assignee | Title |
|---|---|---|---|---|
| GB1480333A (en) * | 1973-07-05 | 1977-07-20 | Svenska Rotor Maskiner Ab | Screw rotor machines |
| JPS5629089A (en) * | 1979-08-17 | 1981-03-23 | Hitachi Ltd | Screw compressor |
-
1981
- 1981-09-22 JP JP14882981A patent/JPS5851290A/en active Granted
Also Published As
| Publication number | Publication date |
|---|---|
| JPS5851290A (en) | 1983-03-25 |
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